JP2010210111A - Ejector type decompression device and refrigerating cycle including the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an ejector type decompression device achieving sufficient mixing of a liquid phase fluid including minute air bubbles and a gas phase fluid in a mixing part. <P>SOLUTION: In an ejector device 4, a narrowing passage 412 which is a first passage of a nozzle 410 is provided with: a first inflow port 411 which is opened on the inner peripheral wall face and to which a liquid phase refrigerant from a radiator 3 is made to flow in along the inner peripheral wall face; and a second inflow port 418 which is opened on the inner peripheral wall face located at an axial end on the upstream side and to which gas having lower pressure than that of the liquid phase refrigerant and made to flow in from the first inflow port 411, is made to axially flow in. A throat part 413 which is a second passage of the nozzle 410 is provided with a turning flow suppressing means (resistor 44) for applying resistance when a turning flow formed in the narrowing passage 412 by inflow of the liquid phase refrigerant along the inner peripheral wall face is made to flow through the throat part 413 to disturb the turning flow. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an ejector-type decompression device that is a momentum transporting pump that is a decompression means for decompressing a fluid and that transports fluid by the entrainment action of a working fluid ejected at high speed, and a refrigeration cycle including the ejector-type decompression device.

  The liquid refrigerant ejected from the nozzle in the ejector-type decompression device has a non-uniform droplet size, and due to the inertial force characteristic of the droplet, the particle size is large near the central axis of the passage of the mixing section. There is a tendency that droplets are distributed and droplets having a small particle diameter that are likely to diffuse near the tube wall. On the other hand, since the gas-phase refrigerant sucked from the suction port tends to flow near the tube wall in the mixing section, it is easy to mix with droplets having a small particle size, but sufficiently mixed with droplets having a large particle size. In other words, the liquid refrigerant and the gas-phase refrigerant are not uniformly mixed in the mixing unit.

  Therefore, the ejector-type decompression device as the first prior art is a mixing means for uniformly mixing the liquid refrigerant ejected from the nozzle outlet and the gas-phase refrigerant sucked from the suction opening. A swirler or needle valve disposed in the center is provided (for example, see Patent Document 1).

  In the first prior art, the refrigerant droplets ejected from the nozzle ejection port collide with the swirler or the needle valve, are diffused toward the tube wall in the mixing unit, are refined, and the gas phase is sucked from the suction port. It becomes mixed with the refrigerant. In the first prior art, the efficiency of the ejector is improved by mixing the liquid refrigerant and the gas-phase refrigerant in the mixing section.

  However, in such a system in which the droplets of the refrigerant are refined in the mixing section, there is a limit to the miniaturization of the liquid refrigerant, and it is necessary to further promote the miniaturization of the liquid refrigerant. In order to promote further miniaturization of the liquid refrigerant, after the refrigerant has passed through the small passage cross-sectional area (also referred to as the throat) in the nozzle, bubbles are grown in the liquid refrigerant by decompression and expansion. It is conceivable to generate fine droplets by promoting the division of the liquid refrigerant.

  As a second conventional technique for generating fine bubbles in the liquid, Patent Document 2 discloses that each swirl flow of the separated liquid and gas is ejected into a stationary liquid, so that the fine liquid is generated in the liquid. A swirl type fine bubble generating device for generating various bubbles is disclosed.

  In this swirl type fine bubble generator, a liquid is introduced from a passage extending in a tangential direction with respect to a space formed by a conical inner wall surface that is tapered on the downstream side to form a swirl flow of liquid in the space, A negative pressure portion is formed on the conical tube axis by the swirling flow. By this negative pressure portion, gas is sucked from the gas inlet provided in the bottom of the conical space. The swirl speed and axial velocity of the liquid increase toward the jet outlet provided at the top of the cone. With this swirl, the centrifugal force acts on the liquid and the centripetal force on the gas due to the specific gravity difference between the liquid and gas. Therefore, the swirling gas portion and the swirling liquid portion can be separated, and the swirling gas portion is formed in a thread shape up to the ejection port. The swirling gas portion is suddenly weakened by the surrounding stationary liquid at the same time as being ejected from the spout, and a rapid swirling speed is generated before and after that. Due to this turning speed difference, the filamentous gas portion is continuously and stably cut, and as a result, a large amount of fine bubbles are generated.

JP-A-6-2964 JP 2003-205228 A

  When the second prior art is applied to an ejector-type decompression device, since no stationary liquid exists at the outlet of the conical space, a swirling flow also exists in the mixing portion downstream of the nozzle. It will be. Due to this swirl flow, the fluid containing bubbles ejected from the nozzle is separated into gas and liquid, and therefore, there is a problem that the fluid sucked from the suction port is not uniformly mixed.

  The present invention has been made in view of the above problems, and an ejector-type decompression device capable of sufficiently mixing a liquid-phase fluid containing fine bubbles and a gas-phase fluid in a mixing section, and a refrigeration cycle having the same The purpose is to provide.

  In order to achieve the above object, the following technical means are adopted. In addition, the code | symbol in the parenthesis as described in a claim and each means of the following shows the correspondence with the specific means as described in embodiment mentioned later as one aspect.

  That is, the invention relating to the ejector-type decompression device according to claim 1 is characterized in that the nozzle (410) for decompressing and expanding the inflowing liquid phase fluid and the gas phase fluid having a pressure lower than the inflowing liquid phase fluid are ejected from the nozzle. A suction port (416) that is sucked by the suction force of the fluid ejected from the outlet (415), and a passage provided on the downstream side of the nozzle ejection port, and the fluid ejected from the nozzle and the suction port A mixing section (42) that constitutes a passage for mixing the gas phase fluid, and a diffuser section (43) that is provided on the downstream side of the mixing section and decelerates the fluid flowing out of the mixing section to increase the pressure. It is equipped with.

The nozzle further includes a first passage (412), which is an upstream passage, whose passage cross-sectional area narrows toward the downstream, a second passage (413) connected to the downstream end of the first passage, and a second passage. A third passage (414) connected to the downstream end of the passage and having a passage cross-sectional area that increases toward the downstream,
The first passage opens to the inner peripheral wall surface of the first passage, and the first inflow port (411) into which the liquid phase fluid flows along the circumferential direction of the inner peripheral wall surface, and the axial direction on the upstream side of the first passage A second inlet (418) that opens to the inner wall surface located at the end and into which a gas phase fluid having a lower pressure than the liquid phase fluid flowing from the first inlet into the first passage flows in the axial direction of the first passage. And are provided,
The second passage is provided with a swirl flow suppressing means (44) that provides resistance when the swirl flow formed in the first passage flows through the second passage by the inflow of the liquid phase fluid along the inner peripheral wall surface and disturbs the swirl flow. ) Is provided.

  According to the present invention, the swirling flow suppressing means provided in the second passage prevents the swirling flow flowing through the second passage, so that the swirling flow is not formed in the downstream third passage and the mixing portion. Therefore, separation of the gas phase fluid and the liquid droplet due to the action of the centrifugal force of the swirling flow does not occur. Thereby, the fine bubbles and liquid phase fluid generated in the nozzle and the low-pressure gas phase fluid sucked from the suction port can be diffused and mixed with each other. Therefore, due to the generation of a large number of bubbles and the effect of suppressing the swirling flow, the liquid phase fluid containing fine bubbles and the gas phase fluid can be sufficiently mixed in the mixing section, and the efficiency of the ejector device can be improved.

  According to a second aspect of the present invention, the swirling flow suppressing means according to the first aspect of the present invention is a resistor (44) provided with a groove (441) formed on the inner wall surface of the second passage. It is provided so that it may advance toward the downstream side while rotating in the direction of rotation opposite to the direction of rotation of the swirl flow traveling downstream in the second passage.

  According to this invention, the groove formed on the inner wall surface of the second passage is provided so as to advance downstream while rotating in the direction opposite to the rotation direction of the swirling flow, so that the swirling flow is near the inner wall surface. Since the circumferential motion of this is subjected to resistance by the groove, the circumferential velocity vector is attenuated. Furthermore, when this state continues on the downstream side, the swirl flow is eliminated in the third passage and the mixing section. Furthermore, the configuration of the groove portion is also useful in that it can provide resistance necessary for suppressing swirling flow without giving extra resistance to the fluid flowing through the second passage.

  According to a third aspect of the present invention, the swirl flow suppressing means in the first aspect of the present invention is a resistor (44A) having an opening (441A) that forms a passage sectional area smaller than that of the second passage. It is characterized by that.

  According to this invention, when the swirling flow that has flowed into the second passage passes through the opening having a passage cross-sectional area smaller than that of the second passage, the swirling flow collides with a wall constituting the surrounding resistor. Thereby, the velocity vector in the circumferential direction of the swirling flow can be attenuated with a simple configuration in the production of narrowing the opening.

  The invention according to claim 4 is the invention according to claim 3, characterized in that the openings (441A, 441B) provided in the resistor (44A, 44B) are slit-shaped. According to the present invention, by forming the opening with an elongated gap, the swirling flow can collide with the wall constituting the resistor around the gap to attenuate the circumferential velocity vector of the swirling flow.

  The invention according to claim 5 is the invention according to claim 3, wherein the opening (441C, 441D) provided in the resistor (44C, 44D) includes a circular central portion and a slit extending radially from the central portion. It is comprised by the shape part. According to the present invention, the opening is formed by the circular opening and the elongated gap extending radially, so that the swirling flow collides with the wall constituting the resistor around the opening to cause the circumferential velocity of the swirling flow. The vector can be attenuated. Furthermore, since the liquid containing fine bubbles flowing near the center axis of the passage easily passes through the circular opening at the center, the passage resistance can be reduced and energy loss can be suppressed.

  The invention according to claim 6 is characterized in that, in the invention according to claim 3, the opening (441E) provided in the resistor (44E) is formed of a concavo-convex portion in which the peripheral edge of the opening is continuous. To do. According to the present invention, since the opening is an opening surrounded by an uneven portion that is continuous in the circumferential direction, the swirling flow collides with the uneven portion in the vicinity of the inner peripheral surface portion of the second passage. The velocity vector in the direction can be attenuated. Furthermore, since the liquid phase fluid containing fine bubbles that flow closer to the center axis of the passage easily passes through the opening inside the uneven portion, the passage resistance can be reduced and energy loss can be suppressed.

  The invention according to claim 7 is the invention according to claim 3, wherein the resistor (44F) includes a wall portion protruding toward the center of the passage. According to the present invention, the swirling flow can collide with the wall portion projecting toward the center of the passage to attenuate the circumferential velocity vector of the swirling flow. Further, the balance between the passage resistance and the swirl flow suppression effect can be easily adjusted by adjusting the protruding length and quantity of the wall portion.

The invention relating to the refrigeration cycle according to claim 8 includes a compressor (2) that sucks and compresses the gas-phase refrigerant, a radiator (3) that radiates and cools the refrigerant discharged from the compressor, The refrigerant cooled by the radiator and the gas-phase refrigerant having a pressure lower than that of the refrigerant are mixed, the gas-liquid mixed refrigerant flows out, and the refrigerant from the radiator is decompressed and expanded. The ejector-type decompression device (4) according to the above section, a gas-liquid separator (5) that separates the gas-liquid mixed refrigerant from the ejector-type decompression device into a gas-phase refrigerant and a liquid-phase refrigerant, and a gas-liquid separation A decompressor (6) for decompressing the liquid-phase refrigerant separated by the evaporator, and an evaporator (7) for exchanging heat with the air to evaporate the liquid-phase refrigerant decompressed by the decompressor,
In the ejector-type decompression device,
The refrigerant cooled by the radiator flows into the first inlet,
At least one of the gas-phase refrigerant separated by the gas-liquid separator and the gas-phase refrigerant evaporated by the evaporator flows into the second inlet.

  According to the present invention, the gas-phase refrigerant introduced into the nozzle for generating fine bubbles can be appropriately selected from the gas-liquid separator and the evaporator in accordance with the operation state of the refrigeration cycle, and the flow rate thereof. Can be increased or decreased. Therefore, in order to improve the efficiency of the ejector device, a refrigeration cycle that effectively utilizes the gas-phase refrigerant present in the cycle can be obtained.

  A ninth aspect of the present invention is the first aspect of the invention according to the eighth aspect, wherein the first vapor phase refrigerant passage for communicating the vapor phase refrigerant portion in which the vapor phase refrigerant of the gas-liquid separator is accommodated with the second inlet. (10) and a second gas-phase refrigerant passage (11) for communicating the evaporator and the second inlet, each having a flow rate adjusting means (12, 13) for adjusting the flow rate of the circulating refrigerant. To do.

  According to the present invention, the amount of bubbles generated at the nozzle and the amount of liquid-phase refrigerant flowing from the evaporator into the nozzle can be adjusted in accordance with the operating state of the refrigeration cycle. Accordingly, it is possible to provide a refrigeration cycle that can respond to various operation requirements, for example, when priority is given to securing gas-phase refrigerant sucked from the evaporator to the suction port, or when it is desired to increase the amount of bubbles.

It is the schematic diagram which showed an example of the vapor compression refrigeration cycle in which the ejector apparatus which is an example of this invention is used. It is typical sectional drawing which showed the structure of the ejector apparatus of 1st Embodiment. It is the front view which showed the turning flow suppression means with which the ejector apparatus of 1st Embodiment is provided. It is the front view which showed the 1st example of the swirl | vortex flow suppression means of 2nd Embodiment. It is the front view which showed the 2nd example of the swirl | vortex flow suppression means of 2nd Embodiment. It is the front view which showed the 1st example of the turning flow suppression means of 3rd Embodiment. It is the front view which showed the 2nd example of the swirl flow suppression means of 3rd Embodiment. It is the front view which showed the turning flow suppression means of 4th Embodiment. It is the front view which showed the swirl | vortex flow suppression means of 5th Embodiment.

  A plurality of modes for carrying out the present invention will be described below with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only a part of the configuration is described in each mode, the other modes described above can be applied to the other parts of the configuration. Not only combinations of parts that clearly show that combinations are possible in each embodiment, but also combinations of the embodiments even if they are not specified unless there is a problem with the combination. Is also possible.

(First embodiment)
1st Embodiment which is one Embodiment of this invention is described using FIGS. 1-3. FIG. 1 shows an example of a vapor compression refrigeration cycle provided with an ejector-type decompression device (ejector device 4). The vapor compression refrigeration cycle 1 includes a compressor 2, a radiator 3 that cools the refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 2 and outdoor air, and a downstream side of the radiator 3. An ejector device 4 as a decompression device that decompresses and expands the high-pressure refrigerant; an evaporator 7 that exchanges heat between the air and the liquid-phase refrigerant; a gas-liquid separator 5 that separates the refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant; Each component is connected by piping. In the present embodiment, for example, carbon dioxide (refrigerant) is used as the fluid circulating in the cycle, and the high-pressure refrigerant discharged from the compressor 2 has a critical pressure or higher. The arrows in FIG. 1 indicate the flow of the refrigerant in the cycle.

  The compressor 2 is driven by an electric motor to suck, compress, and discharge the refrigerant, and can variably control the discharge refrigerant temperature or the discharge refrigerant pressure to be a predetermined value. The compressor 2 is driven by a vehicle running engine via an electromagnetic clutch and a belt, for example, a swash plate type variable displacement compressor capable of continuously variably controlling the discharge capacity by an external control signal. It may be configured.

  The radiator 3 is a heat exchanger that cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 2 and outside air that is forcibly blown by a blower (not shown). For example, when the radiator 3 is used for a hot water heater, the radiator 3 is a water / refrigerant heat exchanger, and hot water is supplied by exchanging heat between the high-pressure refrigerant discharged from the compressor 2 and hot water. It is heated and the refrigerant is cooled.

  The ejector device 4 sucks the gas-phase refrigerant evaporated in the evaporator 7 by decompressing and expanding the mainstream refrigerant (liquid) flowing through the refrigerant passage 8 connected to the radiator 3, and pressure the expansion energy. The suction pressure of the compressor 2 is increased by converting into energy. Further, the ejector device 4 forms a main flow refrigerant in a swirl flow in the nozzle 410 and takes in a gaseous gas phase refrigerant having a lower pressure than the main flow refrigerant (liquid). Circulate the pressure part.

  The gas-liquid separator 5 is a separating unit that separates the refrigerant flowing out from the ejector device 4 into a gas-phase refrigerant and a liquid-phase refrigerant and stores the refrigerant. The gas-phase refrigerant part of the gas-liquid separator 5 in which the gas-phase refrigerant is accumulated is connected to the suction side of the compressor 2 and the inside of the nozzle 410 of the ejector device 4. The liquid-phase refrigerant part of the gas-liquid separator 5 in which the liquid refrigerant accumulates is connected to the inlet of the evaporator 7. A fixed throttle unit 6 (pressure reduction device) is provided between the liquid phase refrigerant unit and the evaporator 7, and the liquid phase refrigerant flowing out from the liquid phase refrigerant unit of the gas-liquid separator 5 is decompressed by the throttle unit 6. To the evaporator 7.

  The evaporator 7 evaporates the liquid phase refrigerant by exchanging heat between the liquid phase refrigerant in the gas-liquid separator 5 decompressed by the throttle unit 6 and the air forcedly blown by a blower (not shown). And a heat exchanger that cools the air and provides cooling capability. The outlet of the evaporator 7 is connected to a suction port 416 that communicates with the periphery of the nozzle 410 of the ejector device 4 and an axial end on the upstream side of the nozzle 410. That is, the gas-phase refrigerant evaporated by the evaporator 7 is introduced into at least one of the periphery of the nozzle 410 and the inside of the nozzle 410.

  The vapor compression refrigeration cycle 1 includes a first gas-phase refrigerant passage 10 that communicates the gas-phase refrigerant portion in which the gas-phase refrigerant of the gas-liquid separator 5 is accommodated with the second inlet 418, an evaporator 7 outlet, And a second gas-phase refrigerant passage 11 that communicates with the second inlet 418. The first gas phase refrigerant passage 10 is provided with a flow rate adjusting valve 12 as a flow rate adjusting means for adjusting the flow rate of the circulating refrigerant, and the second gas phase refrigerant passage 11 is also provided with a flow rate adjusting valve 13 as a flow rate adjusting means. Is provided. The second gas-phase refrigerant passage 11 is a passage that branches from the refrigerant passage 9 that connects the outlet of the evaporator 7 and the suction port 416 to the second inlet 418.

  The operations of the flow rate adjustment valve 12 and the flow rate adjustment valve 13 are controlled by a control device (not shown), and the opening range in which each passage can be opened and closed is freely adjustable in the range of 0% to 100%. The control device adjusts the opening degree of the flow rate adjusting valve 12 or the flow rate adjusting valve 13, so that the vapor phase refrigerant from the vapor phase refrigerant portion of the gas-liquid separator 5 or the vapor phase refrigerant from the evaporator 7 is contained in the nozzle 410. The amount of bubbles generated in the nozzle 410 can be controlled by adjusting the amount taken into the nozzle 410.

  Next, as an example of an ejector-type decompression device, an ejector device 4 that is installed with its axial direction aligned with the horizontal direction will be described in detail with reference to FIGS. FIG. 2 is a schematic cross-sectional view showing the internal configuration of the ejector device 4. As shown in FIG. 2, the ejector device 4 includes a suction unit 41, a mixing unit 42, and a diffuser unit 43 (a boosting unit). The suction part 41 is a suction that sucks the gas-phase refrigerant from the evaporator 7 by the suction force of the nozzle 410 that decompresses and expands the refrigerant that has flowed in and the liquid refrigerant that is formed in the body 40 and ejected from the ejection port 415 of the nozzle 410. And an opening 416, which is a portion disposed on one inlet side of the body 40 of the ejector device 4.

  The mixing portion 42 is a portion disposed in the central portion of the body 40 in the axial direction, and is a passage provided on the downstream side of the ejection port 415 of the nozzle 410, and includes a liquid refrigerant including bubbles ejected from the nozzle 410. A passage for mixing the gas-phase refrigerant sucked from the suction port 416 is configured. The mixing unit 42 is also a flow path provided on the downstream side of the suction port 416, and a high-speed refrigerant flow from the nozzle 410 and the refrigerant sucked from the suction port 416 are mixed, and the diffuser unit 43 is further downstream. Connected with.

  The diffuser portion 43 is a portion disposed on the other outlet side of the body 40, and is formed in a shape in which the passage cross-sectional area gradually increases, and acts to decelerate the refrigerant flow and increase the refrigerant pressure, that is, It has a function of converting the velocity energy of the refrigerant into pressure energy. The mixing unit 42 and the diffuser unit 43 can also be collectively referred to as a boosting unit. The outlet 431 on the downstream side of the diffuser part 43 is connected to the gas phase refrigerant part of the gas-liquid separator 5 arranged on the downstream side in the refrigerant flow direction via a refrigerant pipe.

  The suction port 416 of the suction unit 41 is arranged by shifting the introduction direction of the low-pressure gas-phase refrigerant from the evaporator 7 with respect to the axis of the nozzle 410 and is substantially orthogonal to the axis of the nozzle 410 ( The body 40 is provided so that the refrigerant flows in the substantially orthogonal direction (including the orthogonal direction). The suction port 416 of the body 40 is connected to a low-pressure side refrigerant pipe that forms a refrigerant passage 9 for taking in the gas-phase refrigerant that has flowed out of the evaporator 7. The low-pressure gas-phase refrigerant in the evaporator 7 is sucked into the suction port 416 by the refrigerant jetted from the jet port 415 of the nozzle 410 and flows into the passage 417 formed between the outer periphery of the nozzle 410 and the body. It is introduced to the periphery of the nozzle 410 along the inner peripheral surface of 40. The low-pressure gas-phase refrigerant flows down so as to approach the axial center of the mixing unit 42 while turning around the nozzle 410 so as to draw an arc along the inner peripheral surface of the body 40.

  The nozzle 410 includes a narrowing passage 412 as a first passage, a small-diameter passage 413 (hereinafter also referred to as a throat 413) as a second passage, and an expansion passage 414 as a third passage. The narrowing passage 412 is a passage on the upstream side of the nozzle 410, and the cross-sectional area of the passage is gradually narrowed toward the upstream side. In other words, the narrowing passage 412 is a passage that forms a conical space that tapers toward the downstream. The small-diameter passage 413 is a passage that is connected to the downstream end of the narrow passage 412 and forms a constant passage cross-sectional area. The expansion passage 414 is a passage that is connected to the downstream end portion of the small-diameter passage 413 and is formed so that the passage sectional area gradually increases toward the downstream. In other words, the expansion passage 414 is a passage that forms an inverted conical space that expands toward the downstream.

  The narrow passage 412 that is the first passage opens to the inner peripheral wall surface thereof, and the first inlet through which the liquid-phase refrigerant (high-pressure liquid) from the radiator 3 flows in along the circumferential direction of the inner peripheral wall surface. 411 is provided. Further, the narrow passage 412 opens to an inner wall surface located at the axial end on the upstream side of the narrow passage 412, and is a gas phase refrigerant having a lower pressure than the liquid refrigerant flowing into the narrow passage 412 from the first inlet 411. A second inflow port 418 is provided in which (low pressure gas) narrows and flows in the axial direction of the passage 412.

  The first inflow port 411 is connected to a high-pressure side refrigerant pipe that forms a refrigerant passage 8 for taking in a high-pressure liquid-phase refrigerant that has flowed out of the radiator 3. The second inflow port 418 includes a refrigerant pipe that forms a first gas-phase refrigerant passage 10 for taking in a low-pressure gas-phase refrigerant that has flowed out of the gas-phase refrigerant portion of the gas-liquid separator 5, and a low-pressure that has flowed out of the evaporator 7. And a refrigerant pipe forming a second gas phase refrigerant passage 11 for taking in the gas phase refrigerant. The outlet of the expansion passage 414 is the most downstream end of the nozzle 410 and is the jet outlet 415 of the nozzle 410.

  The high-pressure liquid-phase refrigerant that has flowed into the first inflow port 411 through the refrigerant passage 8 narrows and advances in the axial direction of the nozzle 410 while turning in the passage 412. The low-pressure gas-phase refrigerant from at least one of the gas-liquid separator 5 and the evaporator 7 is drawn from the second inlet 418 into the negative pressure portion near the center axis of the passage formed by the swirling flow of the liquid-phase refrigerant, and the bubbles are evacuated. It progresses in the axial direction of the nozzle 410 with the swirl flow while being generated. And the refrigerant | coolant containing a bubble flows through the narrow path | pass 412, the small diameter channel | path 413, and the expansion channel | path 414 in order, and is decompressively expanded by isentropic.

  Thus, in the ejector device 4, the pressure at the inlet of the nozzle 410 is rapidly decompressed and expanded in the nozzle 410, and the refrigerant has the lowest pressure at the outlet of the nozzle 410. The refrigerant jetted from the jet nozzle 415 of the nozzle 410 is mixed with the gas-phase refrigerant sucked from the suction port 416 in the mixing unit 42, so that the pressure rises gently, and further rises due to the deceleration in the diffuser unit 43. To come.

  The bubbles generated in the nozzle 410 will be described. In the narrowed passage 412 in the nozzle 410, liquid phase refrigerant is introduced from the refrigerant passage 8 extending in the tangential direction, and a spiral flow (swirl flow) is formed that flows down along the inner peripheral wall surface by centrifugal force. By this swirling flow, a negative pressure portion is formed on the axial center of the narrowing passage 412. By this negative pressure portion, the gas-phase refrigerant is sucked from the second inlet 418 provided at the bottom of the conical space. The swirling speed and the axial speed of the liquid phase refrigerant are narrowed and increase toward the downstream end of the passage 412, and with this swirl, centrifugal force acts on the liquid phase refrigerant due to the difference in specific gravity between the liquid and the gas, and the gas phase Since the centripetal force acts on the refrigerant, the swirling gas portion and the swirling liquid portion are separated, and the swirling gas portion is narrowed and formed into a thread shape up to the downstream end of the passage 412.

  When the swirling gas portion is narrowed and ejected from the passage 412 and enters the small diameter passage 413, the thread-like portion is finely cut to generate a large number of fine bubbles. Due to the generation of a large number of fine bubbles, it is possible to promote the division of the liquid-phase refrigerant due to the bubbles. When the breakup of the liquid phase refrigerant is promoted, fine droplets are generated, which activates the mixing of the liquid phase refrigerant and the low-pressure gas-phase refrigerant in the mixing unit 42, thereby achieving uniform mixing of the liquid and the gas. , Ejector efficiency is improved.

  The swirling flow formed by the narrowing passage 412 (first passage) continues even though the turning radius of the small diameter passage 413 (second passage) decreases. Due to the swirling flow in the second passage, due to the characteristics of inertial force, a liquid portion having a large specific gravity swirls near the inner peripheral wall of the passage, and a large number of bubbles exist near the central axis of the passage. Thus, since the liquid part and gas part of a refrigerant | coolant are isolate | separated, both mixing does not become active in a 2nd channel | path. This causes the same phenomenon in the downstream third passage, and further prevents uniform mixing with the gas-phase refrigerant sucked from the suction port 416 in the downstream mixing portion 42. Therefore, the liquid refrigerant and the gas-phase refrigerant are not uniformly mixed in the mixing unit 42, and the efficiency of the ejector cannot be sufficiently ensured.

  Therefore, the ejector device 4 is provided with a swirl flow suppressing means in the small diameter passage 413 that gives resistance when the swirl flow flows and disturbs the formation of the swirl flow. As shown in FIGS. 2 and 3, the swirl flow suppressing means is provided as a resistor 44 so as to occupy at least a part of the axial length of the small diameter passage 413 as the second passage. FIG. 3 is a front view showing an example of the resistor 44 (swirl flow suppressing means) provided in the ejector device 4, and is a view of the section taken along the line III-III in FIG. In FIG. 3, in order to make the resistor 44 easy to see, the expanded passage 414 is not shown, and only the small diameter passage 413 is shown.

  The resistor 44 is a restraining swirl flow restraining means that prevents the swirling flow flowing through the small diameter passage 413 and stops the swirling flow, and is provided with a predetermined length in the axial direction. A groove 441 formed on the wall surface is provided. The groove portion 441 is provided so as to advance toward the downstream side while rotating in the rotation direction opposite to the rotation direction of the swirling flow that travels through the small diameter passage 413 toward the downstream side. In other words, the resistor 44 includes a peak portion 442 projecting inward on the passage center axis side and a valley portion 443 adjacent to the peak portion 442 in the axial direction in the inner peripheral wall portion forming the small diameter passage 413. It is configured. The peak portions 442 are formed at a predetermined pitch in the axial direction, and are provided so as to advance spirally in the axial direction while rotating in a rotational direction opposite to the rotational direction of the swirl flow. The trough 443 is a portion that is recessed outward in the radial direction, is formed at a predetermined pitch with respect to the axial cross section, and is adjacent to the crest 442 and spirals in the axial direction while rotating in the same rotational direction as the crest 442. It is provided to move forward.

  That is, the swirl flow formed by the narrowing passage 412 and flowing into the small-diameter passage 413 collides with the peak portion 442 and the valley portion 443 that form a spiral in the rotation direction opposite to the rotation direction. Directional movement is limited. The resistor 44 provides resistance to the swirling flow in this way. For example, if the rotational direction of the swirling flow is the right-handed screw direction toward the downstream side, the rotation direction of the groove 441 is set to be the left-handed screw direction, and conversely the rotational direction of the swirling flow is the left-handed screw direction. If there is, the rotation direction of the groove 441 is set to be the direction of the left-hand thread.

  For example, for such a resistor 44, a tube material having a predetermined axial length corresponding to the axial length of the resistor 44 is prepared, and the groove portion 441 is processed by cutting or the like on the inner peripheral wall portion of the tube material. It is manufactured by. The tube material with the groove 441 formed is set between two nozzles divided between two nozzles and sandwiched by nozzles divided from both sides in the axial direction, and these three members are brazed and welded (TIG welding, arc welding). , Spot welding, etc.). In this manner, the nozzle 410 in which the resistor 44 is disposed in the small diameter passage 413 is manufactured. Further, the resistor 44, the nozzle 410, the body 40 and the like are formed of the same material, for example, a stainless steel material such as SUS304, SUS316, and SUS310.

  Next, the operation of the vapor compression refrigeration cycle 1 in the above configuration will be described. When a control device (not shown) energizes the electromagnetic clutch of the compressor 2, the electromagnetic clutch is in a connected state, and a rotational driving force is transmitted to the compressor 2 from, for example, a vehicle travel engine. When the compressor 2 is activated, the gas-phase refrigerant is sucked into the compressor 2 from the gas-phase refrigerant portion of the gas-liquid separator 5, and the compressed refrigerant is discharged toward the radiator 3. The high-pressure refrigerant discharged from the compressor 2 flows into the radiator 3 where heat is exchanged with the outdoor air to dissipate and cool. The cooled refrigerant flows into the ejector device 4 from the first inlet 411 of the nozzle 410.

  The liquid-phase refrigerant that has flowed into the nozzle 410 from the first inlet 411 is narrowed to form a swirling flow in the passage 412 (first passage), and flows down by forming a negative pressure portion in the vicinity of the passage center axis. At least one of the gas-phase refrigerant from the gas-liquid separator 5 and the gas-phase refrigerant from the evaporator 7 is sucked into the negative pressure portion through the second inlet 418. The gas-phase refrigerant flowing in from the second inlet 418 flows down the negative pressure portion while forming a swirling flow, and flows into the throat portion 413 (second passage) together with the swirling flow of the liquid phase refrigerant. The narrow throat 413 collides with each other, and the swirling flow of the gas-phase refrigerant is finely broken to generate fine bubbles.

  In the throat 413, since the swirl flow continues and the refrigerant flows down, a large number of bubbles and the liquid-phase refrigerant tend to be separated under the influence of centrifugal force. Therefore, the swirling flow flowing down the throat 413 is prevented from moving in the circumferential direction by the groove 441 functioning as an obstacle on the inner peripheral wall when passing through the resistor 44, and the rotating flow is attenuated as it flows down. Is done. When the swirling flow is attenuated in this way, the centrifugal force is reduced, and a large number of bubbles and the liquid-phase refrigerant are not separated, and both are sufficiently diffused and mixed. For this reason, in the spreading passage 414 (third passage), the droplets do not swirl, and a large number of bubbles grow vigorously due to the decompression and expansion. 42 is released.

  The liquid-phase refrigerant and the gas-phase refrigerant that have flowed into the nozzle 410 in this manner are converted into velocity energy by the nozzle 410, areentropically depressurized by the nozzle 410, and expand, and then the liquid refrigerant and the gas-phase refrigerant are discharged from the nozzle 415. The refrigerant is ejected at a high speed. At this time, the vapor phase refrigerant (low-pressure refrigerant) is sucked into the suction port 416 from the evaporator 7 by the suction action of the refrigerant flow ejected at a high speed. As described above, since the low-pressure gas-phase refrigerant sucked from the evaporator 7 and the fine droplets generated by the growth of many bubbles are uniformly mixed after the mixing unit 42, the efficiency of the ejector is improved. be able to.

  The gas-phase refrigerant and the liquid-phase refrigerant mixed in the mixing part 42 flow into the diffuser part 43, and the speed (expansion) energy of the refrigerant is converted into pressure energy by expanding the passage area of the diffuser part 43. The pressure increases. Then, the refrigerant that has flowed out from the outlet 431 of the diffuser portion 43 flows into the gas-liquid separator 5. The gas-phase refrigerant separated in the gas-liquid separator 5 is sucked into the compressor 2 and recompressed. The liquid-phase refrigerant separated by the gas-liquid separator 5 is decompressed by the throttle unit 6 and then flows into the evaporator 7 to exchange heat with room air and evaporate to cool the room air and provide cooling capacity. The flow rate is adjusted by the flow rate adjusting valve 12 to flow toward the second inflow port 418 and flow down either or both of the routes that contribute to the generation of bubbles.

  Next, an operation for adjusting the amount of bubbles generated in the nozzle 410 will be described. In the first operation, the compressor 2 is started, the flow control valve 12 is opened by the control device, and the flow control valve 13 is controlled to be closed. Thereby, the gas-phase refrigerant separated by the gas-liquid separator 5 is sucked into the compressor 2 and recompressed, and the gas-phase refrigerant flows down through the first gas-phase refrigerant passage 10 and from the second inlet 418 to the nozzle 410. It is divided into those that are inhaled. The gas-phase refrigerant sucked into the nozzle 410 from the second inlet 418 flows down while turning around the negative pressure portion of the passage 412, and becomes finer bubbles at the throat 413, contributing to improvement of the efficiency of the ejector. To do. In addition, the gas-phase refrigerant evaporated in the evaporator 7 is sucked into the ejector device 4 from the suction port 416 and is uniformly mixed in the mixing unit 42 with the droplets that are refined by the generation of fine bubbles. That is, in the first operation, the amount of bubbles increases by the amount of the gas-phase refrigerant in the gas-liquid separator 5 that has flowed into the second inlet 418, and all the gas-phase refrigerant evaporated in the evaporator 7 42 is used for a gas phase refrigerant mixed with droplets. As described above, the gas-phase refrigerant of the gas-liquid separator 5 is sucked into the second inlet 418 because the gas-phase refrigerant has a higher pressure than the gas-phase refrigerant evaporated in the evaporator 7, and the narrow passage 412. This is because the pressure difference between the negative pressure portion and the negative pressure portion is easy to be taken, so that it is easy to suck into the nozzle 410 and the suction efficiency is good.

  Next, in the second operation, the compressor 2 is started, and the flow rate adjusting valve 12 and the flow rate adjusting valve 13 are controlled to be opened by the control device. As a result, the gas-phase refrigerant evaporated by the evaporator 7 in the first operation further flows down through the second gas-phase refrigerant passage 11 and flows into the nozzle 410 through the second inlet 418. That is, the gas-phase refrigerant evaporated in the evaporator 7 is sucked into the ejector device 4 from the suction port 416, and sucked into the nozzle 410 from the second inlet 418 through the second gas-phase refrigerant passage 11. It is divided into what is done. The gas-phase refrigerant in the gas-liquid separator 5 and a part of the gas-phase refrigerant evaporated in the evaporator 7 are sucked into the nozzle 410 from the second inlet 418 and flow down while turning around the negative pressure portion of the narrow passage 412. In addition, the air bubbles are made finer at the throat 413, which contributes to improving the efficiency of the ejector. Further, the remaining gas-phase refrigerant evaporated in the evaporator 7 is sucked into the ejector device 4 from the suction port 416 and is uniformly mixed with the droplets which are made fine by the generation of fine bubbles in the mixing unit 42. That is, in the second operation, the amount of bubbles is equal to the total amount of the gas-phase refrigerant of the gas-liquid separator 5 flowing into the second inlet 418 and a part of the gas-phase refrigerant evaporated in the evaporator 7. Compared with the operation of 1, it is greatly increased. Thus, the second operation is control that is selected when it is desired to increase the amount of bubbles.

  In addition to the first and second operations described above, a third operation may be performed. In the third operation, the compressor 2 is started, the flow control valve 12 is closed by the control device, and the flow control valve 13 is controlled to be open. As a result, all the gas-phase refrigerant separated by the gas-liquid separator 5 is sucked into the compressor 2 and recompressed. Further, the gas-phase refrigerant evaporated in the evaporator 7 is sucked into the ejector device 4 from the suction port 416, and is sucked into the nozzle 410 from the second inlet 418 through the second gas-phase refrigerant passage 11. It is divided into what is done. That is, only a part of the gas-phase refrigerant evaporated in the evaporator 7 is sucked into the nozzle 410 from the second inlet 418 and flows down while turning around the negative pressure portion of the narrowing passage 412 and refined in the throat 413. Contributes to improving the efficiency of the ejector. Further, the remaining gas-phase refrigerant evaporated in the evaporator 7 is sucked into the ejector device 4 from the suction port 416 and is uniformly mixed with the droplets which are made fine by the generation of fine bubbles in the mixing unit 42. As described above, in the third operation, the amount of bubbles is increased only by a part of the gas-phase refrigerant evaporated in the evaporator 7 and the amount of the gas-phase refrigerant sucked into the compressor 2 can be increased.

  Furthermore, the opening degree of the flow rate adjustment valve 12 and the flow rate adjustment valve 13 is freely adjusted according to the operating state of the refrigeration cycle. This is applied to each of the first operation, the second operation, and the third operation, and an appropriate amount of gas-phase refrigerant can be adjusted in all operations.

  The effect which the ejector apparatus 4 of this embodiment brings is described. The ejector device 4 includes a nozzle 410 that decompresses and expands an inflowing liquid-phase refrigerant (liquid), and a suction force by a fluid in which a gas-phase refrigerant (gas) having a pressure lower than that of the liquid-phase refrigerant is ejected from a nozzle outlet 415. A suction port 416 that is sucked by the nozzle, and a passage provided downstream of the nozzle outlet 415, and a refrigerant (fluid) ejected from the outlet 415 and a gas-phase refrigerant (gas) sucked from the suction port 416 A mixing portion 42 that constitutes a passage for mixing the two, a diffuser portion 43 that is provided on the downstream side of the mixing portion 42 and decelerates the refrigerant (fluid) flowing out from the mixing portion 42 to increase the pressure, Is provided.

  The nozzle 410 includes a narrowing passage 412 (first passage) whose cross-sectional area is narrowed toward the downstream, a small diameter passage 413 (second passage) connected to the downstream end of the narrowing passage 412, and a downstream end of the small diameter passage 413. And an expanded passage 414 (third passage) having a passage cross-sectional area that increases toward the downstream. The narrow passage 412 has openings on the inner peripheral wall surface thereof, a first inlet 411 into which liquid phase refrigerant flows along the inner peripheral wall surface, and an inner wall surface located at the axial end of the narrow passage 412 upstream. There is provided a second inlet 418 that is opened and a gas-phase refrigerant (gas) having a pressure lower than that of the liquid-phase refrigerant flowing in from the first inlet 411 is narrowed and flows in the axial direction of the passage 412. The small diameter passage 413 is provided with a resistor 44 (swirl flow restraining means) that gives resistance when the swirling flow formed by the narrowing passage 412 flows through the small diameter passage 413 and disturbs the swirling flow.

  According to the configuration of the ejector device 4 described above, the flow of the swirling flow that flows through the small diameter passage 413 can be prevented by the resistor 44 provided in the small diameter passage 413. Thereby, since the swirl flow is not formed in the downstream spread 414 and the mixing unit 42, the separation of the gas phase fluid and the liquid droplet due to the action of the centrifugal force of the swirl flow does not occur. Therefore, by generating a large number of bubbles and suppressing the swirling flow in the nozzle 410, fine bubbles and droplets generated in the nozzle 410 and the air from the evaporator 7 sucked from the suction port 416. It is possible to form a flow in which the phase fluid is sufficiently diffused and mixed with each other to improve the efficiency of the ejector device.

  The swirl flow suppressing means is a resistor 44 including a groove portion 441 formed on the inner wall surface of the small diameter passage 413. The groove portion 441 has a spiral shape that advances toward the downstream side while rotating in the direction of rotation opposite to the direction of rotation of the swirling flow that travels downstream through the small diameter passage 413.

  According to this configuration, the groove portion 441 is provided so as to advance downstream while rotating in the direction opposite to the rotation direction of the swirling flow, so that the swirling flow flowing through the small diameter passage 413 is in the circumferential direction near the inner wall surface. The movement is resisted by the groove 441. For this reason, the velocity vector in the circumferential direction is attenuated, and the swirling flow is eliminated in the spreading passage 414 and the mixing unit 42. Moreover, since the groove part 441 is a groove part which can be formed in the inner wall surface of a pipe | tube, the resistance required in order to suppress a swirl flow without giving extra resistance with respect to the fluid which distribute | circulates the small diameter channel | path 413 is easy. Useful in that it can be given to. Moreover, since the groove part 441 can be implemented also by manufacturing an internal thread in the inner wall surface which forms the small diameter channel | path 413, it is preferable on manufacture and can provide the swirl flow suppression means excellent in productivity.

  Further, the resistor 44 has a groove 441, thereby forming a passage that does not become an obstacle near the passage center axis of the small diameter passage 413, and gives resistance only to the fluid flowing near the inner wall surface. For this reason, the bubbles flowing near the central axis of the passage smoothly flow through the passage without receiving resistance, and flow down while mixing with the droplets showing the flow in which the swirling flow is collapsed. In other words, the flow loss in the small diameter passage 413 can be reduced. For this reason, the resistance given to a refrigerant | coolant can be reduced and the flow which suppressed energy loss can be provided.

(Second Embodiment)
In the second embodiment, another form of the swirling flow suppressing means of the first embodiment will be described with reference to FIGS. FIG. 4 is a front view showing a first example of the swirl flow suppressing means of the present embodiment. FIG. 5 is a front view showing a second example of the swirling flow suppressing means of the present embodiment. 4 and 5 are both views of the section taken along the line III-III in FIG. In FIG. 4 and FIG. 5, the components given the same reference numerals as those in the drawings of the first embodiment described above are the same components and have the same effects. 4 and 5, the enlarged passage 414 is not shown, and only the small diameter passage 413 is shown in order to make the resistor easier to see.

  As shown in FIG. 4, the resistor 44 </ b> A, which is a first example of the present embodiment, is a restraining swirl flow restraining means that prevents the swirling flow from flowing through the small diameter passage 413 and stops the swirling flow. An opening 441A that forms a passage cross-sectional area smaller than the passage 413 is provided. The opening 441A has an elongated slit shape and is provided in a predetermined length in the axial direction to form a rectangular parallelepiped passage space. The length of the long side of the slit that forms the opening 441A is equal to the inner diameter of the small diameter passage 413. The opening peripheral edge portion of the opening portion 441A is an end portion of the wall portion protruding inward from the inner wall surface of the small diameter passage 413. The swirling flow that flows into the small-diameter passage 413 collides with the wall portion, and its circumferential movement is limited. The liquid droplet (liquid phase refrigerant) that collided with the wall portion flows along with the fine bubbles through the opening 441A that traverses the central portion of the passage cross section and flows downstream. At this time, since the velocity component in the circumferential direction has disappeared, only the velocity component in the axial direction spreads and flows into the passage 414, and the separation of the droplets and bubbles is eliminated.

  For example, for such a resistor 44A, a pipe material having a predetermined axial length corresponding to the axial length of the resistor 44A is prepared, and a wall portion forming the opening 441A is disposed at a predetermined position inside the pipe material. It is manufactured by joining it to the inner wall surface. The tube material in which the opening 441A is formed is set between nozzles divided into two members, and is sandwiched by nozzles divided from both sides in the axial direction. These three members are brazed and welded (TIG welding, arc Welding, spot welding, etc.) and so on. In this way, the nozzle 410 in which the resistor 44A is disposed in the small diameter passage 413 is manufactured.

  Further, as shown in FIG. 5, the resistor 44 </ b> B as the second example of the present embodiment includes an opening 441 </ b> B whose cross-sectional shape is a cross-shaped slit. The opening 441 </ b> B forms a passage cross-sectional area smaller than the small diameter passage 413. The opening 441B forms a passage space in which a plurality of openings each having a slit shape in a cross-sectional shape intersects radially. Such an opening 441B is provided for a predetermined length in the axial direction, and forms a passage space where a plurality of rectangular parallelepiped spaces intersect. The opening peripheral edge portion of the opening 441B is an end portion of the wall portion that protrudes inward from the inner wall surface of the small diameter passage 413. The swirling flow that flows into the small-diameter passage 413 collides with the wall portion, and its circumferential movement is limited. The liquid droplet (liquid phase refrigerant) colliding with the wall portion flows downstream along with the fine bubbles through the opening 441B that radially traverses the central portion of the passage cross section. At this time, since the velocity component in the circumferential direction has disappeared, only the velocity component in the axial direction spreads and flows into the passage 414, and the separation of the droplets and bubbles is eliminated. The resistor 44B is also manufactured by the same method as the resistor 44A.

  The swirl flow suppressing means of the present embodiment is the resistors 44A and 44B having the openings 441A and 441B that form passage cross-sectional areas smaller than the small diameter passage 413, so that the swirl flow passes through the openings 441A and 441B. When you collide with the surrounding wall. For this reason, the velocity vector in the circumferential direction is attenuated, and the swirling flow is eliminated in the spreading passage 414 and the mixing unit 42. In addition, the swirling flow suppressing means of the present embodiment can realize a resistor with a simple configuration in terms of manufacturing that restricts the opening.

  In addition, since the openings 441A and 441B are slit-shaped, the swirling flow collides against the wall portion around the elongated gap, so that the effect of attenuating the circumferential velocity vector of the swirling flow is great.

(Third embodiment)
In the third embodiment, another form of the swirling flow suppressing means of the first embodiment will be described with reference to FIGS. FIG. 6 is a front view showing a first example of the swirling flow suppressing means of the present embodiment. FIG. 7 is a front view showing a second example of the swirling flow suppressing means of the present embodiment. 6 and 7 are both views of the section taken along the line III-III in FIG. In FIG. 6 and FIG. 7, the components given the same reference numerals as those in the drawings of the first embodiment described above are similar components and have the same operational effects. In FIGS. 6 and 7, the enlarged passage 414 is not shown, and only the small diameter passage 413 is shown in order to make the resistor easier to see.

  As shown in FIG. 6, the resistor 44 </ b> C, which is a first example of the present embodiment, is a restraining swirl flow suppressing means that has a function of preventing the swirl flow that flows through the small-diameter passage 413 and stopping the swirl flow. is there. The opening 441C included in the resistor 44C includes a circular central portion and slit-like portions extending radially from the central portion. The total length of the circular portion and the slit-like portion extending radially from the circular portion is equal to the inner diameter of the small diameter passage 413. The opening 441 </ b> C forms a passage cross-sectional area smaller than the small diameter passage 413. The opening 441C is provided for a predetermined length in the axial direction, and forms a passage space in which a central cylindrical space and two rectangular parallelepiped spaces extending outward from the cylindrical space are combined. The opening peripheral edge portion of the opening 441C is an end portion of the wall portion that protrudes inward from the inner wall surface of the small diameter passage 413. The swirling flow that flows into the small-diameter passage 413 collides with the wall portion, and its circumferential movement is limited. The liquid droplet (liquid phase refrigerant) that collided with the wall portion flows through the opening 441C that crosses the central portion of the passage cross section together with the fine bubbles to the downstream side. At this time, since the velocity component in the circumferential direction has disappeared, only the velocity component in the axial direction spreads and flows into the passage 414, and the separation of the droplets and bubbles is eliminated. The resistor 44C is also manufactured by the same method as the resistor 44A described above.

  Further, as shown in FIG. 7, the resistor 44 </ b> D as the second example of the present embodiment further includes an opening 441 </ b> D having another set of slit-like portions extending radially with respect to the opening 441 </ b> C of the resistor 44 </ b> C. I have. The opening 441D forms a passage cross-sectional area smaller than the small diameter passage 413. The opening 441D is provided for a predetermined length in the axial direction, and forms a passage space in which a central columnar space and four rectangular spaces extending outward from the columnar space are combined. The opening peripheral edge portion of the opening portion 441D is an end portion of the wall portion that protrudes inward from the inner wall surface of the small diameter passage 413. The swirling flow that flows into the small-diameter passage 413 collides with the wall portion, and its circumferential movement is limited. The droplet (liquid phase refrigerant) colliding with the wall portion flows downstream along with the fine bubbles through the opening 441D that radially traverses the central portion of the passage cross section. At this time, since the velocity component in the circumferential direction has disappeared, only the velocity component in the axial direction spreads and flows into the passage 414, and the separation of the droplets and bubbles is eliminated. The resistor 44D is also manufactured by the same method as the resistor 44A.

  The openings 441C and 441D provided in the resistors 44C and 44D of the present embodiment are configured by a circular central portion and slit-like portions extending radially from the central portion. According to this configuration, the openings 441C and 441D through which the refrigerant flows are formed by the circular openings and the elongated gaps that extend radially, so that the swirling flow forms the walls constituting the resistors 44C and 44D around the openings. The velocity vector in the circumferential direction of the swirling flow can be attenuated.

  Furthermore, since a circular opening that does not become an obstacle is formed in the vicinity of the passage center axis of the small diameter passage 413, resistance can be given only to the fluid flowing in the vicinity of the inner wall surface. For this reason, the bubbles flowing near the central axis of the passage smoothly flow through the passage without receiving resistance, and flow down while mixing with the droplets showing the flow in which the swirling flow is collapsed. In other words, the flow loss in the small diameter passage 413 can be reduced. For this reason, the resistance given to a refrigerant | coolant is reduced and the flow which suppressed energy loss can be provided.

(Fourth embodiment)
In the fourth embodiment, another form of the swirl flow suppressing means of the first embodiment will be described with reference to FIG. FIG. 8 is a front view showing the swirl flow suppressing means of the present embodiment, and is a view of the III-III cut surface of FIG. In FIG. 8, components denoted by the same reference numerals as those in the drawing of the first embodiment described above are similar components and exhibit the same operational effects. In FIG. 8, the enlarged passage 414 is not shown, and only the small diameter passage 413 is shown in order to make the resistor easier to see.

  As shown in FIG. 8, the resistor 44E of the present embodiment is a restraining swirl flow suppressing means having a function of preventing the swirl flow flowing through the small diameter passage 413 and stopping the swirl flow. The opening 441E provided in the resistor 44E is an opening formed by a concavo-convex portion having a continuous opening peripheral portion. The concavo-convex part is constituted by a peak part and a valley part arranged at a predetermined pitch in the circumferential direction on the inner peripheral wall part of the small diameter passage 413. In other words, the resistor 44E is composed of a crest projecting inward on the channel central axis side and a trough adjacent to the crest in the axial direction on the inner peripheral wall forming the small-diameter channel 413. Yes. The distance between the two valleys having point symmetry with respect to the center of the passage is equal to the inner diameter of the small diameter passage 413. The opening 441E forms a passage cross-sectional area smaller than the small diameter passage 413. The opening 441 </ b> E is a star-shaped opening on a cut surface that crosses the small diameter passage 413. A plurality of adjacent crests and troughs are extended by a predetermined length in the axial direction.

  The swirling flow that flows into the small-diameter passage 413 collides with the crests and troughs that are continuous in the circumferential direction and extend in the axial direction, and the movement in the circumferential direction is limited. The resistor 44E thus provides resistance to the swirling flow. The liquid droplets (liquid refrigerant) colliding with the crests and troughs that are the peripheral edge of the opening 441E flow downstream along with the fine bubbles through the opening 441E that crosses the center of the passage cross section. At this time, since the circumferential velocity component has disappeared, most of the velocity component spreads with only the axial velocity component and flows into the passage 414, and the separation of the droplets and bubbles is eliminated. The resistor 44E is also manufactured by the same method as the resistor 44A described above.

  The opening 441E provided in the resistor 44E according to the present embodiment is formed of a concavo-convex portion whose peripheral edge is continuous in the circumferential direction. According to this configuration, since the swirling flow passes through the opening surrounded by the continuous uneven portion, the swirling flow collides with the uneven portion in the vicinity of the inner peripheral surface portion of the small diameter passage 413, and the circumferential velocity vector of the swirling flow is set. Can be attenuated.

  Furthermore, since the resistor 44E is formed with an opening that does not become an obstacle inside the passage more than the uneven portion, resistance can be given only to the fluid flowing in the vicinity of the inner wall surface. For this reason, the bubbles flowing near the central axis of the passage smoothly flow through the passage without receiving resistance, and flow down while mixing with the droplets showing the flow in which the swirling flow is collapsed. In other words, the flow loss in the small diameter passage 413 can be reduced. For this reason, the resistance given to a refrigerant | coolant is reduced and the flow which suppressed energy loss can be provided. In other words, the resistor 44E is a swirl flow suppressing means that has an excellent balance between the passage resistance and the effect of suppressing swirl flow and contributes to the adjustment of the balance between the two.

(Fifth embodiment)
In the fifth embodiment, another form of the swirl flow suppressing means of the first embodiment will be described with reference to FIG. FIG. 9 is a front view showing the swirl flow suppressing means of the present embodiment, and is a view of the III-III cut surface of FIG. In FIG. 9, the components denoted by the same reference numerals as those in the drawing of the first embodiment described above are the same components and have the same effects. In FIG. 9, the enlarged passage 414 is not shown, and only the small diameter passage 413 is shown in order to make the resistor easier to see.

  As shown in FIG. 9, the resistor 44 </ b> F of the present embodiment is a restraining swirl flow suppressing means that has a function of preventing the swirl flow that flows through the small diameter passage 413 and stopping the swirl flow. The resistor 44F includes a wall portion that protrudes toward the center of the passage. The opening 441F is an opening formed by the inner peripheral wall surface and the wall portion of the small diameter passage 413. In other words, a wall portion that protrudes inward from the inner peripheral wall surface of the small-diameter passage 413 exists in the circular cross-section passage. The opening 441F forms a passage cross-sectional area smaller than that of the small diameter passage 413. The wall portion is provided in a predetermined length in the axial direction, and an opening 441F corresponding to the same length is provided. The opening 441F extending in the axial direction is a passage space obtained by subtracting a rectangular parallelepiped space occupied by the wall portion from the columnar space.

  The swirling flow flowing into the small-diameter passage 413 collides with a rectangular parallelepiped wall portion extending in the axial direction, and its circumferential movement is limited. The resistor 44F thus provides resistance to the swirling flow. The liquid droplet (liquid phase refrigerant) that collided with the wall portion flows along the fine wall and the downstream side through the opening portion 441F through the wall portion. At this time, since the circumferential velocity component has disappeared, most of the velocity component spreads with only the axial velocity component and flows into the passage 414, and the separation of the droplets and bubbles is eliminated. The resistor 44F is also manufactured by the same method as the resistor 44A described above.

  The resistor 44F of the present embodiment has a configuration including a wall portion that protrudes toward the center of the passage. According to this, the swirling flow can collide with the wall portion protruding in the passage, and the circumferential velocity vector of the swirling flow can be attenuated. Further, by adjusting the protruding length and quantity of the wall portion, resistance can be given only to the fluid flowing near the inner wall surface, and the flow loss in the small diameter passage 413 can be reduced. As a result, bubbles flowing near the center axis of the passage can be smoothly flowed with a small resistance, and can flow down while being mixed with droplets.

(Other embodiments)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

  The swirl flow suppressing means provided in the throat 413 of the nozzle 410 is not limited to the configuration disclosed in the above embodiment. In other words, the swirling flow suppressing means is a resistor that limits the circumferential movement of the swirling flow flowing in the nozzle 410 and attenuates the circumferential velocity component to the extent that the flow separating the gas and the liquid is eliminated. The shape and the like are not limited to the configuration described in the above embodiment.

  In the vapor compression refrigeration cycle 1 of the above embodiment, the flow rate adjusting valve 12 and the flow rate adjusting valve 13 are provided as flow rate adjusting means, but a configuration including only one of the flow rate adjusting valves may be employed.

  In the vapor compression refrigeration cycle 1 of the above-described embodiment, the flow rate adjustment valve 12 and the flow rate adjustment valve 13 are provided, but these flow rate adjustment valves may be replaced with a fixed throttle portion.

  The ejector device 4 in the above embodiment can be applied to a vehicle air conditioner, a heat pump cycle for a water heater or an indoor air conditioner. Moreover, the fixed place of the ejector apparatus 4 may be a moving body such as a vehicle, or may be a fixed object placed at a fixed position.

  Moreover, in the said embodiment, although the fluid which flows in into the ejector-type decompression device is made into the refrigerant | coolant of a carbon dioxide, it is not limited to such a refrigerant | coolant. Further, the refrigeration cycle to which the ejector device 4 is applied may be any one of a supercritical cycle and a subcritical cycle of a vapor compression type such as a fluorocarbon refrigerant, an HC refrigerant, and carbon dioxide.

2 ... Compressor 3 ... Radiator 4 ... Ejector device (Ejector type decompression device)
5 ... Gas-liquid separator 6 ... Throttle part (pressure reduction device)
DESCRIPTION OF SYMBOLS 7 ... Evaporator 10 ... 1st gas-phase refrigerant path 11 ... 2nd gas-phase refrigerant path 12, 13 ... Flow control valve (flow control means)
42 ... mixing part 43 ... diffuser part 44, 44A, 44B, 44C, 44D, 44E, 44F ... resistor (swirl flow suppressing means)
410 ... Nozzle 411 ... First flow port 412 ... Narrow passage (first passage)
413 ... Small diameter passage, throat (second passage)
414 ... Expansion passage (third passage)
Reference numeral 415... Jet 416. Suction opening 418. Second inlet 441. Groove 441 A, 441 B, 441 C, 441 D, 441 E, 441 F.

Claims (9)

A nozzle (410) for decompressing and expanding the inflowing liquid phase fluid;
A suction port (416) in which a gas phase fluid having a pressure lower than that of the inflowing liquid phase fluid is sucked by a suction force generated by the fluid ejected from the nozzle outlet (415);
A mixing portion (42) constituting a passage provided on the downstream side of the nozzle outlet of the nozzle and configured to mix the fluid ejected from the nozzle and the gas-phase fluid sucked from the suction port When,
A passage provided on the downstream side of the mixing unit, the diffuser unit (43) for decelerating the fluid flowing out of the mixing unit and increasing the pressure;
With
The nozzle includes a first passage (412), which is an upstream passage, the passage cross-sectional area of which is narrowed toward the downstream, a second passage (413) connected to a downstream end of the first passage, and the first passage A third passage (414) connected to the downstream end of the two passages and having a passage cross-sectional area that increases toward the downstream,
In the first passage,
A first inlet (411) that opens to the inner peripheral wall surface of the first passage and into which the liquid phase fluid flows along the circumferential direction of the inner peripheral wall surface, and an axial end on the upstream side of the first passage A second inflow port in which a gas phase fluid having a lower pressure than the liquid phase fluid flowing into the first passage from the first inflow port flows in the axial direction of the first passage. 418), and
In the second passage,
A swirl flow restraining means (44) for imparting resistance and disturbing the swirl flow when the swirl flow formed in the first passage flows through the second passage by the inflow of the liquid phase fluid along the inner peripheral wall surface. An ejector-type decompression device characterized by being provided. The swirl flow suppressing means is a resistor (44) including a groove (441) formed on the inner wall surface of the second passage,
2. The groove portion is provided so as to advance toward the downstream side while rotating in a rotation direction opposite to a rotation direction of the swirling flow traveling downstream in the second passage. An ejector-type decompression device as described in 1.   2. The ejector-type pressure reducing device according to claim 1, wherein the swirl flow suppressing means is a resistor (44 </ b> A) having an opening (441 </ b> A) that forms a passage cross-sectional area smaller than the second passage. apparatus.   The ejector-type decompression device according to claim 3, wherein the openings (441A, 441B) provided in the resistor (44A, 44B) are slit-shaped.   The opening (441C, 441D) provided in the resistor (44C, 44D) includes a circular central portion and slit-like portions extending radially from the central portion. An ejector-type decompression device as described in 1.   4. The ejector-type decompression device according to claim 3, wherein the opening (441 </ b> E) provided in the resistor (44 </ b> E) is formed of a concavo-convex portion whose peripheral edge is continuous in the circumferential direction.   The ejector-type decompression device according to claim 3, wherein the resistor (44F) includes a wall portion protruding toward a center of the passage. A compressor (2) for sucking and compressing the gas-phase refrigerant;
A radiator (3) for radiating and cooling the refrigerant discharged from the compressor;
8. The refrigerant cooled by the radiator and a gas-phase refrigerant having a pressure lower than that of the refrigerant are mixed to flow out a gas-liquid mixed refrigerant, and the refrigerant from the radiator is decompressed and expanded. An ejector-type decompression device (4) according to any one of
A gas-liquid separator (5) for separating the gas-liquid mixed refrigerant from the ejector-type decompression device into a gas-phase refrigerant and a liquid-phase refrigerant;
A decompression device (6) for decompressing the liquid-phase refrigerant separated by the gas-liquid separator;
An evaporator (7) for exchanging heat with the air to evaporate the liquid refrigerant decompressed by the decompressor,
In the ejector type decompression device,
The refrigerant cooled by the radiator flows into the first inlet,
At least one of the gas-phase refrigerant separated by the gas-liquid separator and the gas-phase refrigerant evaporated by the evaporator flows into the second inlet.   A first gas-phase refrigerant passage (10) for communicating the gas-phase refrigerant portion of the gas-liquid separator in which the gas-phase refrigerant is accommodated with the second inlet, and the evaporator and the second inlet; The refrigeration cycle according to claim 8, further comprising a flow rate adjusting means (12, 13) for adjusting the flow rate of the circulating refrigerant in each of the second gas-phase refrigerant passages (11) that communicate with each other.

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