JP2008107054A - Pressure reducing device and refrigerating cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve cycle efficiency of a refrigerating cycle device by improving a pressure reducing efficiency ηn of a pressure reducing device. <P>SOLUTION: In this ejector type refrigerating cycle device where the flow of refrigerant is branched at a downstream side of a radiator 12, a swirl flow generation branch portion 15 for swirling the flow of refrigerant flowing into a fixed throttle 19 and a fixed nozzle portion 20a of an ejector 20 is disposed at a downstream side of the radiator 12. By the swirl flow, the boiling of the liquid-phase refrigerant in the fixed throttle 19 and the fixed nozzle portion 20a is promoted to improve the pressure reducing efficiency ηn, and specific enthalpy of the refrigerant after expansion under reduced pressure is lowered, thus the cycle efficiency (COP) is improved. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a decompression device that decompresses and expands refrigerant in a refrigeration cycle device, and a refrigeration cycle device to which the decompression device is applied.

  Conventionally, Patent Document 1 discloses a decompression device (electronic expansion valve) that decompresses and expands refrigerant in a refrigeration cycle apparatus. The pressure reducing device of Patent Document 1 includes a needle valve that is a pressure reducing portion configured to be able to change a refrigerant passage area, and a flow of refrigerant that is disposed upstream of the needle valve and is decompressed by the needle valve in the axial direction of the needle. It has a swirl flow generating part (refrigerant inflow chamber) that swirls around.

Then, the swirl flow generation unit swirls the refrigerant flow and flows into the decompression unit to avoid the refrigerant flowing into the decompression unit from directly colliding with the needle, and the vibration generated when the refrigerant collides with the needle. The sound is suppressed. Furthermore, the gas-liquid of the refrigerant is separated by the centrifugal force of the swirling flow, and the liquid-phase refrigerant whose swirling speed is higher than that of the gas-phase refrigerant is actively boiled to reduce the pressure loss due to the expansion of the gas-phase refrigerant. ing.
JP-A-8-159617

By the way, the decompression part of this kind of decompression device changes the pressure energy of the refrigerant into kinetic energy when decompressing and expanding the refrigerant. Therefore, the energy conversion efficiency of the decompression section (hereinafter referred to as decompression efficiency ηn) is defined by the following formula F1.
^{ηn = (Vn 2/2)} / Δien ... (F1)
Vn is the flow rate of the refrigerant after decompression and expansion in the decompression unit, and Δien is the amount of decrease in specific enthalpy when the refrigerant per unit weight is isentropically decompressed and expanded. Further, the pressure reduction efficiency ηn corresponds to what is generally called nozzle efficiency when the pressure reduction portion is formed of a nozzle.

  According to Formula F1, the pressure reduction efficiency ηn can be improved by increasing the flow velocity Vn of the refrigerant after the pressure reduction expansion. Therefore, in the decompression device of Patent Document 1, the pressure loss associated with the expansion of the gas-phase refrigerant can be reduced, and the flow rate of the refrigerant after the decompression and expansion can be increased. Therefore, the decompression efficiency ηn of the decompression unit can be improved. it can.

  Furthermore, if the refrigerant in the decompression and expansion process is made supersonic by improving the decompression efficiency ηn of the decompression unit, the refrigerant can be decompressed and expanded in an isentropic manner, so that the amount of decrease in specific enthalpy when the refrigerant is decompressed and expanded Can be increased.

  Therefore, if the decompression device of patent document 1 is applied to a refrigeration cycle device, the enthalpy difference (refrigeration capacity) of the refrigerant between the inlet and outlet of the evaporator that evaporates the refrigerant after decompression expansion is expanded, and the refrigeration cycle device Cycle efficiency (COP) should be improved.

  However, even if the decompression device of Patent Document 1 is actually applied to the refrigeration cycle device and operated, the cycle efficiency is not improved compared to the case where the decompression device that does not generate a swirl flow in the refrigerant inflow chamber is applied. Then, when the present inventors investigated the cause, it turned out that it is because the pressure reduction part is comprised with the needle valve.

  The reason for this is that when a needle-like valve element (needle) is disposed in the refrigerant passage inside the decompression section like a needle valve, the inner periphery of the refrigerant passage and the outer periphery of the needle are close to each other. This is because the refrigerant swirling along the circumference adheres to the needle and flows along the needle. That is, if the refrigerant flows along the needle, the swirl component is weakened, and the flow rate of the refrigerant cannot be increased sufficiently.

  As a result, in the decompression device of Patent Document 1, the decompression efficiency ηn cannot be sufficiently improved even if the refrigerant flow is swirled upstream of the decompression unit. Furthermore, even if applied to a refrigeration cycle apparatus, the cycle efficiency cannot be sufficiently improved.

  In view of the above points, the first object of the present invention is to improve the decompression efficiency ηn of the decompression device.

  A second object of the present invention is to improve the cycle efficiency (COP) of the refrigeration cycle apparatus.

  The present invention has been devised to achieve the above-described object, and is a decompression device applied to a refrigeration cycle apparatus, comprising a decompression unit (19, 20a) for decompressing and expanding a refrigerant, and a decompression unit (19 , 20a) and a swirl flow generating section (15, 25, 26, 27, 28) that swirls the flow of the refrigerant flowing into the decompression section (19, 20a). 20a) has a first feature that it is configured with a fixed aperture.

  According to this, since the decompression unit (19, 20a) is configured by a fixed throttle, the refrigerant flowing into the decompression unit (19, 20a) is transferred to the needle or the like as in the decompression device described in Patent Document 1. Does not adhere. Accordingly, the gas-liquid refrigerant can be separated by centrifugal force without weakening the swirling flow component of the refrigerant, and the liquid-phase refrigerant having a swirling speed higher than that of the gas-phase refrigerant can be efficiently boiled.

  As a result, the pressure loss due to the expansion of the gas-phase refrigerant can be reduced, and the flow rate of the refrigerant flowing out from the decompression section (19, 20a) can be increased, so the decompression efficiency (ηn) of the decompression section (19, 20a) Can be improved effectively.

  Further, in the decompression device of the first feature, specifically, the swirl flow generating portion (15, 25, 26, 27) includes an inflow passage (16, 25a, 26a, 27a) through which a refrigerant flows and an inflow passage. (16, 25a, 26a, 27a) An outflow passage (17, 18, 25c, 25d, 26c, 26d, 27c) through which the refrigerant flows out in a direction different from the inflow direction of the refrigerant flowing in from (16, 25a, 26a, 27a) may be provided.

  Thus, by changing the flow direction of the refrigerant, the refrigerant can be easily swirled, and the swirling flow generators (15, 25, 26, 27) can be easily configured.

  Further, specifically, the swirl flow generating portions (25, 27) have cylindrical swirl tube portions (25b, 27b) for swirling the refrigerant therein, and the inflow passages (25a, 27a) are swirl tubes. The refrigerant may flow in the circumferential direction of the parts (25b, 27b), and the outflow passages (25c, 25d, 27c) may flow the refrigerant in the axial direction of the swivel cylinder parts (25b, 27b).

  Further, in the decompression device of the first feature, specifically, the swirl flow generation unit (28) has a refrigerant passage (28a) for allowing the refrigerant to flow in and out, and an inner wall surface of the refrigerant passage (28a) includes: A spiral groove (28b) may be formed. Thus, even if the spiral groove (28b) is formed on the inner wall surface of the refrigerant passage (28a), the refrigerant can be easily swirled.

  Moreover, in this invention, let the refrigerating cycle apparatus provided with the decompression device of the above-mentioned 1st characteristic be the 2nd characteristic. According to this, the cycle efficiency (COP) of the refrigeration cycle apparatus can be improved by improving the decompression efficiency (ηn) of the decompression unit (19, 20a).

Moreover, in this invention, the compressor (11) which compresses and discharges a refrigerant | coolant, The heat radiator (12) which radiates the high temperature / high pressure refrigerant | coolant discharged from the compressor (11), and a radiator (12) exit side refrigerant | coolant The refrigerant is sucked into the refrigerant suction port (20b) by a high-speed refrigerant flow injected from a branch part (Z) that branches the flow of the refrigerant and a fixed nozzle part (20a) that decompresses and expands one of the refrigerants branched at the branch part (Z). ), An ejector (20) that mixes the high-speed refrigerant flow and the refrigerant sucked from the refrigerant suction port (20b) and pressurizes the diffuser part (20c), and is branched at the branch part (Z) A fixed throttle (19) for decompressing and expanding the other refrigerant, and a suction side evaporator (23) for evaporating the refrigerant on the downstream side of the fixed throttle (19) and flowing out to the upstream side of the refrigerant suction port (20b),
Nozzle side swirl flow generators (16, 18, 25b, 26b) that are arranged downstream of the branch part (Z) and upstream of the fixed nozzle part (20a) and swirl the flow of the refrigerant flowing into the fixed nozzle part (20a). 27b, 28), and a throttle side swirl flow generator (16, which is arranged downstream of the branch part (Z) and upstream of the fixed throttle (19) and swirls the flow of the refrigerant flowing into the fixed throttle (19) A refrigeration cycle apparatus including at least one of 17, 25b, 26b, 27b, and 28) is a third feature.

  According to this, at least one of the nozzle part side swirl flow generator (16, 18, 25b, 26b, 27b, 28) and the nozzle part side swirl flow generator (16, 17, 25b, 26b, 27b, 28). Therefore, at least one of the ejector (20) and the fixed throttle (19) can be configured in the same manner as the decompression means of the first feature. Therefore, the cycle efficiency (COP) of the refrigeration cycle apparatus can be improved by improving the pressure reduction efficiency (ηn) of at least one of the fixed nozzle portion (20a) and the fixed throttle (19).

  Here, the cycle efficiency improvement effect of the refrigeration cycle apparatus of the third feature will be described with reference to the Mollier diagram of FIG. 4 shows the state of the refrigerant in the refrigeration cycle apparatus according to the first embodiment of the present invention, which will be described later, by a solid line, the nozzle part side swirl flow generator (16, 18, 25b, 26b, 27b, 28) and the throttle side. The state of the refrigerant in the comparative refrigeration cycle apparatus (hereinafter simply referred to as the comparative example apparatus) that is not provided with any of the swirling flow generators (16, 17, 25b, 26b, 27b, 28) is indicated by a broken line.

  First, in the refrigeration cycle apparatus of the third feature, the nozzle section side swirl flow generator (16, 18, 25b, 26b, 27b, 28) is provided, so that the fixed nozzle section (20a) is compared with the comparative apparatus. It is possible to increase the flow rate of the refrigerant flow injected from the air.

  Thereby, the decompression / expansion process of the refrigerant (point e → f in FIG. 4) in the fixed nozzle part (20a) of the refrigeration cycle apparatus of the third feature is changed to the decompression / expansion process of the fixed nozzle part (20a) of the comparative example apparatus. In contrast to (point e → f ′ in FIG. 4), it is possible to approach the isentropic line shown by the two-dot chain line in FIG. Therefore, in the refrigeration cycle apparatus of the third feature, the specific enthalpy of the refrigerant after decompression and expansion can be reduced by Δi1 relative to the comparative example apparatus.

  Furthermore, the refrigerant suction amount sucked from the refrigerant suction port (20b) can be increased by sufficiently increasing the flow rate of the refrigerant flow injected from the fixed nozzle portion (20a). As a result, the amount of energy recovered by the ejector 20 can be increased, and as shown in FIG. 4, the pressure increase amount ΔP of the refrigerant in the diffuser section (20d) can also be increased relative to the pressure increase amount ΔP ′ in the comparative apparatus.

  As a result, since the suction pressure of the compressor (11) can be increased, the driving power of the compressor (11) can be reduced and the cycle efficiency can be improved.

  Next, in the refrigeration cycle device of the third feature, the fixed nozzle portion (20a) is provided with respect to the comparative example device by including the throttle side swirl flow generator (16, 17, 25b, 26b, 27b, 28). It is possible to increase the flow rate of the refrigerant flow injected from the air.

  As a result, the decompression / expansion process of refrigerant in the fixed throttle (19) of the refrigeration cycle apparatus according to the third feature (point e → k in FIG. 4) is changed to the decompression / expansion process (fig. 4 point e → k ′ point), the isentropic line shown by the two-dot chain line in FIG. 4 can be approximated. Therefore, in the refrigeration cycle apparatus of the third feature, the specific enthalpy of the refrigerant after decompression and expansion can be reduced by Δi2 relative to the comparative apparatus.

  As a result, the enthalpy difference (refrigeration capacity) of the refrigerant between the inlet and outlet in the suction side evaporator (23) can be expanded, and the cycle efficiency can be improved.

  In the refrigeration cycle apparatus having the third feature, the ejector (20) may include an outflow side evaporator (21) for evaporating the outflow refrigerant.

  As described above, in the refrigeration cycle apparatus of the third feature, the specific enthalpy of the refrigerant after decompression and expansion can be decreased by Δi1 relative to the comparative example apparatus, so that the inlet / outlet in the outflow evaporator (21) can be reduced. Cycle efficiency can be improved by expanding the enthalpy difference (refrigeration capacity) of the refrigerant between the outlets.

  In the refrigeration cycle apparatus having the third feature described above, the nozzle side swirl flow generator (16, 18, 25b, 26b, 27b, 28) and the throttle swirl flow generator (16, 17, 25b, 26b, 27b and 28) may be provided.

  In the refrigeration cycle device having the third feature described above, the nozzle side swirl flow generator (16, 18, 25b, 26b), the throttle side swirl flow generator (16, 17, 25b, 26b) and the branching unit ( Z) may be integrally configured as a swirl flow generation branch (15, 25, 26). According to this, it is possible to reduce the size of the refrigeration cycle apparatus.

  The swirl flow generation branching section (15, 25, 26) has a function as a branching section for branching the refrigerant flow and a function as a swirling flow generation section for swirling the refrigerant flow flowing out from the branching section. It means a bifurcation with swirl flow generation function.

  More specifically, the swirl flow generation branching section (15, 25, 26) branches from the inflow passage (16, 25a, 26a) through which the refrigerant flows and the inflow passage (16, 25a, 26a). A first outflow passage (17, 25c, 26c) for flowing out, and a second outflow passage (18, 25d, 26d) for branching out of the inflow passage (16, 25a, 26a) and flowing out the refrigerant, The outflow passages (17, 25c, 26c) and the second outflow passages (18, 25d, 26d) allow the refrigerant to flow out in a direction different from the flow direction of the refrigerant flowing into the inflow passages (16, 25a, 26a). It may be.

  According to this, the refrigerant can be easily swirled by changing the flow direction of the refrigerant, and the swirl flow generation branching portions (15, 25, 26) can be easily configured.

  Furthermore, the axial directions of the inflow passage (16), the first outflow passage (17), and the second outflow passage (18) are arranged on the same horizontal plane, and the first outflow passage (17) has a passage diameter (φd2) and a first direction. The passage diameter (φd3) of the two outflow passages (18) may be formed larger than the passage diameter (φd1) of the inflow passage (16).

  According to this, the flow diameter (φd2) of the first outflow passage (17) and the flow diameter (φd3) of the second outflow passage (18) are formed larger than the flow diameter (φd1) of the inflow passage (16). Therefore, the refrigerant flowing from the inflow passage (16) into the first outflow passage (17) and the second outflow passage (18) can be easily swirled.

  Further, since the axial directions of the inflow passage (16), the first outflow passage (17), and the second outflow passage (18) are arranged on the same horizontal plane, the influence of gravity is exerted when the refrigerant flow is branched. It becomes hard to receive and can branch a refrigerant appropriately. In the present invention, the term “same horizontal plane” does not mean only completely identical horizontal planes, but also includes slightly different planes caused by processing errors and assembly errors.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is an overall configuration diagram of an example in which the refrigeration cycle apparatus of the present invention is applied to a vehicle air conditioner. In addition, the refrigerating cycle apparatus 10 of this embodiment is an ejector type refrigerating cycle apparatus provided with the ejector 20, as shown in FIG.

  First, in the refrigeration cycle apparatus 10, the compressor 11 sucks, compresses and discharges refrigerant, and is driven to rotate by a driving force transmitted from a vehicle travel engine (not shown) via a pulley and a belt. .

  The compressor 11 may be a variable capacity compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or a fixed capacity type compressor that adjusts the refrigerant discharge capacity by changing the operating rate of the compressor operation by switching the electromagnetic clutch. Any of the machines may be adopted. Further, if an electric compressor is used as the compressor 11, the refrigerant discharge capacity can be adjusted by adjusting the rotation speed of the electric motor.

  A radiator 12 is connected to the refrigerant discharge side of the compressor 11. The radiator 12 is a cooling heat exchanger that cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and outside air (air outside the vehicle compartment) blown by a cooling fan (not shown).

  In the ejector refrigeration cycle of the present embodiment, a chlorofluorocarbon refrigerant is employed as the refrigerant, and a subcritical cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant is configured. Therefore, the radiator 12 acts as a condenser that condenses the refrigerant.

  A liquid receiver 12 a is connected to the outlet side of the radiator 12. The liquid receiver 12a has a vertically long tank shape, and functions as a gas-liquid separator that separates the gas-liquid refrigerant and accumulates excess liquid-phase refrigerant in the cycle. In the present embodiment, the liquid receiver 12 a is provided integrally with the radiator 12.

  Further, as the radiator 12, a heat exchanger for condensation located on the upstream side of the refrigerant flow, a receiver for separating the gas and liquid of the refrigerant by introducing the refrigerant from the heat exchanger for condensation, and the receiver A so-called subcool type condenser having a supercooling heat exchanging section for supercooling the saturated liquid phase refrigerant from may be adopted.

  A liquid phase refrigerant outlet through which the liquid phase refrigerant flows out is provided on the bottom side of the liquid receiver 12a, and the high pressure side refrigerant flow path 13a of the internal heat exchanger 13 is connected to the liquid phase refrigerant outlet. . The internal heat exchanger 13 performs heat exchange between the radiator 12 outlet side refrigerant passing through the high pressure side refrigerant flow path 13a and the compressor 11 suction side refrigerant passing through the low pressure side refrigerant flow path 13b.

  As the specific configuration of the internal heat exchanger 13, various configurations can be adopted, but in the present embodiment, a double-pipe heat exchanger configuration is adopted. More specifically, the inner pipe that forms the low-pressure side refrigerant flow path 13b is arranged inside the outer pipe that forms the high-pressure side refrigerant flow path 13a.

  An expansion valve 14 is connected to the outlet side of the high-pressure side refrigerant flow path 13a of the internal heat exchanger 13. The expansion valve 14 is a pressure reducing means for reducing the high-pressure liquid-phase refrigerant flowing out from the liquid receiver 12a to an intermediate pressure, and is also a flow rate adjusting means for adjusting the flow rate of the refrigerant flowing out downstream. As the expansion valve 14, an electric flow rate adjusting valve capable of variably controlling the refrigerant passage area, a fixed flow rate adjusting valve, or the like can be employed.

  On the downstream side of the expansion valve 14, a function as a branching portion for branching the refrigerant flow, and a swirling flow generator for swirling the refrigerant flow flowing into the fixed throttle 19 and the fixed nozzle portion 20 a of the ejector 20 described later. A swirl flow generating branching section 15 having a function is connected. Details of the swirl flow generation branching section 15 will be described with reference to FIGS. FIG. 2 is a schematic perspective view of the swirl flow generating / branching portion 15, and FIG. 3 is a cross-sectional view taken along the line AA of FIG.

  The swirl flow generation branching section 15 includes an inflow pipe 16 (inflow passage) for allowing refrigerant to flow in, and a first outflow pipe 17 (first outflow path) for branching from the inflow pipe 16 to flow out the refrigerant to the fixed throttle 19 side described later. And a second outflow pipe 18 (second outflow passage) that branches from the inflow pipe 16 and flows the refrigerant out to the fixed nozzle portion 20a side of the ejector 20 described later.

  Furthermore, the axial directions of the first outflow pipe 17 and the second outflow pipe 18 are perpendicular to the axial direction of the inflow pipe 16, and the inflow pipe 16, the first outflow pipe 17, and the second outflow pipe 18. The axial direction is arrange | positioned on the same horizontal surface.

  In this way, the refrigerant flow direction can be changed by allowing the refrigerant flowing in from the inflow pipe 16 to flow out from the first outflow pipe 17 and the second outflow pipe 18, so that the thick arrows B and C in FIG. As shown, the refrigerant flow can be easily swirled.

  That is, when the refrigerant, which has been decompressed by the expansion valve 14 and is in a gas-liquid two-phase state, flows from the inflow pipe 16 into the first outflow pipe 17 and the second outflow pipe 18, the influence of inertial force on the vapor phase refrigerant. The liquid refrigerant that is susceptible to flow tends to flow along the inner wall surfaces of the first outflow pipe 17 and the second outflow pipe 18. Thereby, the flow of the refrigerant can be easily swirled.

  Therefore, in the present embodiment, the branch portion Z that branches the refrigerant flow is formed at the connection portion between the inflow pipe 16 and the first outflow pipe 17, and the throttle side swirl flow is generated by the inflow pipe 16 and the first outflow pipe 17. The inflow pipe 16 and the second outflow pipe 18 constitute a nozzle part side swirl flow generator. That is, the nozzle side swirl flow generator, the throttle side swirl flow generator, and the branch part Z are integrally configured as a swirl flow generation branch part 15.

  3, the passage diameter φd2 of the first outflow pipe 17 is larger than the passage diameter φd1 of the inflow pipe 16, and the passage diameter φd3 of the second outflow pipe 18 is larger than that of the inflow pipe 16. It is formed larger than the passage diameter φd1. 3 is a vertical sectional view of the inflow pipe 16 in the axial direction. Thereby, the refrigerant that has flowed from the inflow pipe 16 into the first outflow pipe 17 and the second outflow pipe 18 is easily swirled.

  Furthermore, by arranging the axial directions of the inflow pipe 16, the first outflow pipe 17 and the second outflow pipe 18 on the same horizontal plane, the first outflow pipe is less affected by gravity when the refrigerant flow is branched. By merely adjusting the pipe diameter φd2 of the pipe 17 and the pipe diameter φd3 of the second outflow pipe 18, the amount of refrigerant flowing out to the outflow pipes 17 and 18 can be appropriately distributed.

  Such a swirl flow generation / branching portion 15 can be easily formed by joining refrigerant pipes having different diameters by joining means such as brazing, welding, and adhesion. Furthermore, you may form by providing a some refrigerant path in the inside of a rectangular parallelepiped metal block or resin block.

  Next, as shown in FIG. 1, the first outflow pipe 17 of the swirl flow generation branch section 15 is connected to the fixed throttle 19, and the second outflow pipe 18 is connected to the fixed nozzle section 20 a of the ejector 20. The ejector 20 is a pressure reducing means for reducing the pressure of the refrigerant, and is also a refrigerant circulating means for circulating the refrigerant by a suction action of the refrigerant flow injected at a high speed.

  Further, the ejector 20 includes a fixed nozzle portion 20a which is a pressure reducing portion for reducing the passage area of the intermediate pressure refrigerant flowing in from the second outflow pipe 18 to reduce the refrigerant further, and a refrigerant injection port of the fixed nozzle portion 20a. It arrange | positions so that it may connect and it has the refrigerant | coolant suction opening 20b which attracts | sucks the refrigerant | coolant which flowed out from the suction side evaporator 23 mentioned later.

  The fixed nozzle portion 20a is a nozzle having a fixed refrigerant passage area. That is, the refrigerant passage area is not configured to be changeable. Therefore, the inflow pipe 16, the second outflow pipe 18 and the fixed nozzle 20a constituting the nozzle-side swirl flow generator described above realize the same configuration as the decompression device of the first feature of the present invention.

  In the present embodiment, a Laval nozzle having a throat portion with the smallest passage area in the middle of the refrigerant passage is employed as the fixed nozzle 20a. Of course, a tapered nozzle may be adopted as the fixed nozzle portion 20a.

  Further, the ejector 20 mixes the high-speed refrigerant flow injected from the refrigerant injection port of the fixed nozzle portion 20a and the suction refrigerant sucked from the refrigerant suction port 20b downstream of the fixed nozzle portion 20a and the refrigerant suction port 20b. And a diffuser portion 20d that forms a pressure increasing portion on the downstream side of the mixing portion 20c.

  The diffuser portion 20d is formed in a shape that gradually increases the refrigerant passage area, and functions to decelerate the refrigerant flow to increase the refrigerant pressure, that is, to convert the velocity energy of the refrigerant into pressure energy. Further, the outlet side of the diffuser portion 20 d is connected to the outflow side evaporator 21.

  The outflow side evaporator 21 performs heat exchange between the refrigerant flowing out from the diffuser portion 20d of the ejector 20 and the air blown by a blower fan (not shown), and evaporates the low-pressure refrigerant to exert an endothermic effect. It is a heat exchanger. Furthermore, the outlet side of the outflow side evaporator 21 is connected to the inlet side of the low-pressure side refrigerant flow path 13b of the internal heat exchanger 13 described above.

  Further, an accumulator 22 is connected to the outlet side of the low-pressure side refrigerant flow path 13b. The accumulator 22 is a gas-liquid separator that separates the refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant, and the gas-phase refrigerant outlet of the accumulator 22 is connected to the refrigerant suction side of the compressor 11.

  Next, the first outlet pipe 17 is connected to the inlet side of the fixed throttle 19, and the outlet side of the fixed throttle 19 is connected to the suction side evaporator 23. The fixed throttle 19 is a pressure reducing unit that depressurizes the refrigerant flowing into the suction side evaporator 23 and has a flow rate adjusting function for adjusting the flow rate of the refrigerant flowing into the suction side evaporator 23.

  In the present embodiment, a capillary tube is employed as the fixed throttle 19. Therefore, the inflow pipe 16, the first outflow pipe 17 and the fixed throttle 19 constituting the throttle side swirl flow generator described above realize the same configuration as the decompression device of the first feature of the present invention.

  The suction side evaporator 23 is a heat absorption heat exchanger that performs heat exchange between the refrigerant flowing out of the fixed throttle 19 and the blower fan blown air to evaporate the low-pressure refrigerant and exert an endothermic action. Here, the outflow side evaporator 21 is disposed on the upstream side (windward side) in the flow direction of the air blown by the blower fan, and the suction side evaporator 23 is disposed on the downstream side (downwind side) in the air flow direction. ing.

  Furthermore, in this embodiment, the outflow side evaporator 21 and the suction side evaporator 23 are assembled into an integral structure. Specifically, the constituent parts of the outflow side evaporator 21 and the suction side evaporator 23 are made of aluminum and joined to an integral structure by brazing.

  Therefore, the air blown from the above-described blower fan flows in the direction of arrow Y, and is first cooled by the outflow side evaporator 21 and then cooled by the suction side evaporator 23. That is, the same cooling target space (vehicle interior) can be cooled by the outflow side evaporator 21 and the suction side evaporator 23.

  Next, the operation of the present embodiment in the above-described configuration will be described with reference to FIG. FIG. 4 is a Mollier diagram schematically showing the state of the refrigerant in the refrigeration cycle apparatus 10. In FIG. 4, the solid line indicates the state of the refrigerant in the refrigeration cycle apparatus 10 of the present embodiment, and the broken line indicates the state of the refrigerant in the comparative apparatus described later.

  First, in this embodiment, when the compressor 11 is driven by a vehicle engine, the compressor 11 sucks in refrigerant, compresses it, and discharges it. The state of the refrigerant at this time is point a in FIG. The high-temperature and high-pressure gas-phase refrigerant discharged from the compressor 11 flows into the radiator 12 and radiates heat by exchanging heat with the blown air (outside air) blown from the cooling fan (point a → b in FIG. 4). .

  The refrigerant flowing out of the radiator 12 is gas-liquid separated in the liquid receiver 12a (point b → c in FIG. 4), and the separated liquid phase refrigerant flows into the high-pressure side refrigerant flow path 13a of the internal heat exchanger 13. To do. The liquid-phase refrigerant that has flowed into the high-pressure side refrigerant flow path 13a is cooled by exchanging heat with the refrigerant sucked by the compressor 11 passing through the low-pressure side refrigerant flow path 13b, and enters a supercooled state (point c → d in FIG. 4). ).

  The refrigerant that has flowed out of the high-pressure side refrigerant flow path 13a flows into the expansion valve 14, is reduced to an intermediate pressure, and enters a gas-liquid two-layer state (point d → point e in FIG. 4). The refrigerant in the gas-liquid two-layer state is branched at a branch portion Z (point e in FIG. 4) of the swirl flow generation branch portion 15, and one of the branched refrigerants is fixed through a first outlet pipe 17. The other refrigerant flows into the fixed nozzle portion 20 a of the ejector 20 through the second outflow pipe 18.

  The refrigerant flowing into the fixed nozzle portion 20a of the ejector 20 is decompressed and expanded in an isentropic manner (point e → point f in FIG. 4). And the pressure energy of a refrigerant | coolant is converted into speed energy at the time of this decompression | expansion expansion, and a refrigerant | coolant is injected at high speed from the refrigerant | coolant injection port of the fixed nozzle part 20a. Due to the refrigerant suction action of the injected refrigerant, the refrigerant after passing through the suction side evaporator 23 is sucked from the refrigerant suction port 20b.

  Then, in the ejector 20, the injection refrigerant injected from the fixed nozzle portion 20a and the suction refrigerant sucked from the refrigerant suction port 20b are mixed in the mixing portion 20c (point f → point g in FIG. 4), and the diffuser portion 20d. In the diffuser portion 20d, the passage energy is increased and the velocity energy of the refrigerant is converted into pressure energy, so that the pressure of the refrigerant increases (point g → point h in FIG. 4).

  The refrigerant flowing out of the diffuser portion 20d of the ejector 20 flows into the outflow side evaporator 21, absorbs heat from the blown air of the blower fan, and evaporates (point h → point i in FIG. 4). Further, the refrigerant that has flowed out of the outflow side evaporator 21 flows into the low pressure side refrigerant flow path 13b of the internal heat exchanger 13 and is heated by exchanging heat with the high pressure refrigerant that passes through the high pressure side refrigerant flow path 13a ( I point in FIG. 4 → j point).

  The refrigerant heated in the low-pressure side refrigerant flow path 13b of the internal heat exchanger 13 is drawn into the compressor 11 from the gas-phase refrigerant outlet of the accumulator 22 and is compressed again (point j → point a in FIG. 4).

  On the other hand, the refrigerant that has flowed into the fixed throttle 19 via the first outlet pipe 17 is decompressed by the fixed throttle 19 to become a low-pressure refrigerant (point e → point k in FIG. 4). Flow into. The refrigerant that has flowed into the suction side evaporator 23 absorbs heat from the air after heat exchange in the outflow side evaporator 21 and evaporates (point k → l in FIG. 4). The gas-phase refrigerant after passing through the suction-side evaporator 23 is sucked into the ejector 20 from the refrigerant suction port 20b (point l → g in FIG. 4).

  As described above, in the present embodiment, the refrigerant on the downstream side of the diffuser portion 20d of the ejector 20 is supplied to the outflow side evaporator 21, and is supplied to the suction side evaporator 23 via the refrigerant on the downstream side of the throttle means 20. The outflow side evaporator 21 and the suction side evaporator 23 can exhibit a cooling action simultaneously.

  Further, the same cooling target space can be cooled by passing the air blown from the blower fan in the order of the outflow side evaporator 21 → the suction side evaporator 23. At this time, the refrigerant evaporation pressure (refrigerant evaporation temperature) of the suction-side evaporator 23 can be made lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the outflow-side evaporator 21 by the suction action of the ejector 20. And the temperature difference of the refrigerant | coolant evaporation temperature of the suction side evaporator 23 and blowing air is ensured, and blowing air can be cooled efficiently.

  Further, since the downstream side of the outflow side evaporator 21 is connected to the suction side of the compressor 11, the refrigerant whose pressure has been increased by the diffuser portion 20 d of the ejector 20 can be sucked into the compressor 11. Thereby, since the suction pressure of the compressor 11 can be raised, the drive power of the compressor 11 can be reduced.

  Further, the action of the internal heat exchanger 13 can expand the refrigerant enthalpy difference (refrigeration capacity) between the inlet and outlet in the outflow side evaporator 21 and the suction side evaporator 23, so that the cycle refrigeration capacity can be increased to increase the cycle. Efficiency (COP) can be improved.

  Furthermore, in this embodiment, since the swirl | flow flow generation | occurrence | production branch part 15 is employ | adopted, the high cycle efficiency improvement effect can be acquired. This cycle efficiency improvement effect will be described in comparison with the cycle efficiency improvement effect of the comparative apparatus.

  First, the comparative example device is a refrigeration cycle device that does not include the swirl flow generation branching unit 15, that is, the nozzle unit side swirl flow generator and the throttle side swirl flow generator, and specifically, swirl flow generation. The branch part 15 is changed to a three-way joint, and the other configuration is the same as that of the refrigeration cycle apparatus 10 of the present embodiment.

  Therefore, when the comparative apparatus is operated, the refrigerant flows in the order of the compressor 11 → the radiator 12 → the liquid receiver 12a → the internal heat exchanger 13 → the expansion valve 14 and is configured by a three-way joint, as in the present embodiment. The branch is made at the branch portion Z (point a → b point → c point → d point → e point in FIG. 4). Then, the refrigerant flowing into the fixed nozzle portion 20a from the branch portion Z is decompressed and expanded in an isentropic manner as indicated by point e → f ′ in FIG.

  Further, the injection refrigerant and the suction refrigerant are mixed in the mixing unit 20c of the ejector 20 (point f ′ → g ′ in FIG. 4) and raised in the diffuser section 20d (point g ′ → h ′ in FIG. 4). ). And it flows in order of the outflow side evaporator 21-> internal heat exchanger 13-> accumulator 22-> compressor 11 (h 'point-> i' point-> j 'point-> a point of FIG. 4).

  On the other hand, the refrigerant flowing into the fixed throttle 19 from the branch part Z is decompressed by the fixed throttle 19 to become a low-pressure refrigerant (point e → k ′ in FIG. 4), and the suction side evaporator 23 → the ejector 20 (refrigerant drinking) Mouth 20b) flows in the order (k point → l point → g ′ point in FIG. 4).

  Here, the decompression / expansion process of the refrigerant in the fixed nozzle part 20a of this embodiment (point e → f in FIG. 4) and the decompression / expansion process of the fixed nozzle part 20a of the comparative apparatus (point e → f ′ in FIG. 4). 4), as shown in FIG. 4, in the present embodiment, the decompression and expansion process of the refrigerant in the fixed nozzle portion 20a can be made closer to the isentropic line indicated by a two-dot chain line.

  The reason for this is that in this embodiment, the flow of the refrigerant is swirled and flows into the fixed nozzle portion 20a, so that the boiling of the liquid-phase refrigerant is promoted and the flow velocity of the refrigerant is sufficiently increased with respect to the comparative apparatus. This is because the pressure reduction efficiency (nozzle efficiency) ηn of the fixed nozzle portion 20a can be improved.

  At this time, since the decompression unit is configured by the fixed nozzle 20a, the refrigerant flowing into the decompression unit does not adhere to the needle or the like as in the decompression device described in Patent Document 1. Accordingly, the gas-liquid refrigerant can be separated by centrifugal force without weakening the swirling flow component of the refrigerant, and the liquid-phase refrigerant having a swirling speed higher than that of the gas-phase refrigerant can be efficiently boiled.

  As a result, in this embodiment, as shown in FIG. 4, the specific enthalpy of the refrigerant after decompression and expansion can be reduced by Δi1 with respect to the comparative apparatus, so that the inlet / outlet in the outflow evaporator 21 can be reduced. The refrigerant enthalpy difference (refrigeration capacity) can be expanded.

  Furthermore, the refrigerant suction amount sucked from the refrigerant suction port 20b can be increased by sufficiently increasing the flow rate of the refrigerant flow injected from the fixed nozzle portion 20a. As a result, the amount of energy recovered by the ejector 20 can be increased, and as shown in FIG. 4, the pressure increase amount ΔP of the refrigerant in the diffuser portion 20d also increases with respect to the pressure increase amount ΔP ′ in the comparative apparatus.

  As a result, in the present embodiment, the suction pressure of the compressor 11 can be increased with respect to the comparative example device, so that the driving power of the compressor 11 can be reduced.

  Further, the decompression / expansion process of the refrigerant in the fixed throttle 19 of this embodiment (point e → k in FIG. 4) and the decompression / expansion process of the fixed throttle 19 of the comparative apparatus (point e → k ′ in FIG. 4). In comparison, as shown in FIG. 4, in the present embodiment, the decompression and expansion process of the refrigerant in the fixed throttle 19 can be brought close to an isentropic line indicated by a two-dot chain line.

  The reason is that in the present embodiment, the flow of the refrigerant is swirled and flows into the fixed throttle 19, so that the flow rate of the refrigerant is sufficiently increased with respect to the comparative example device so that the refrigerant in the decompression / expansion process exceeds the refrigerant. This is because the speed of sound can be increased.

  At this time, since the decompression unit is constituted by the fixed throttle 19, the refrigerant flowing into the decompression unit does not adhere to the needle or the like as in the decompression device described in Patent Document 1. Therefore, it is possible to effectively increase the speed of the refrigerant in the decompression / expansion process by reducing the pressure loss due to the expansion of the gas-phase refrigerant without weakening the swirl component of the refrigerant.

  As a result, in this embodiment, as shown in FIG. 4, the specific enthalpy of the refrigerant after decompression and expansion can be reduced by Δi2 with respect to the comparative apparatus, so that the inlet / outlet in the suction-side evaporator 23 can be reduced. The refrigerant enthalpy difference (refrigeration capacity) can be expanded.

  As described above, in the present embodiment, by adopting the swirl flow generation / branching portion 15, the flow of the refrigerant flowing into the fixed nozzle portion 20a and the fixed throttle 19 of the ejector 20 is swirled to improve the pressure reduction efficiency ηn. , The cycle efficiency can be effectively improved.

(Second Embodiment)
In the present embodiment, a refrigeration cycle apparatus that employs a swirl flow generation / branching section 26 shown in FIG. 6 with respect to the swirl flow generation / branching section 15 of the first embodiment will be described. Other configurations are the same as those of the first embodiment.

  FIG. 5 is a schematic perspective view of the swirling flow generating branching section 25. The swirling flow generating branching section 25 has an inflow pipe 25a (inflow passage) through which a refrigerant flows and a cylindrical swirling that swirls the refrigerant inside. The cylinder part 25b, the first outflow pipe 25c (first outflow passage) for allowing the refrigerant to flow out from the swivel cylinder part 25b to the fixed throttle 19 side, and the refrigerant from the swirl cylinder part 25b to the fixed nozzle part 20a side of the ejector 20 A second outlet pipe 25d (second outlet passage) is provided.

  The inflow pipe 25a is connected to the central part of the swivel cylinder part 25b, and is further connected along the outer circumferential tangent direction of the swivel cylinder part 25b. That is, the inflow pipe 25a is configured to allow the refrigerant to flow in the circumferential direction of the swivel cylinder portion 25b.

  Each outflow pipe 25c, 25d is connected to the axial end of the swivel cylinder 25b, and the axial direction of each outflow pipe 25c, 25d and the swivel cylinder 25b are arranged coaxially. Yes. That is, the outflow pipes 25c and 25d are configured to allow the refrigerant to flow out in the axial direction of the swivel cylinder portion 25b.

  Therefore, the refrigerant that has flowed into the swivel cylinder part 25b from the inflow pipe 25a swirls along the inner wall of the swirl cylinder part 25b, and in the swirled state, as shown by the thick line arrows B and C in FIG. , 25d.

  That is, in this embodiment, the branch part Z is formed in the inside of the turning cylinder part 25b, and the turning cylinder part 25b serves as the function of a throttle side turning flow generator and a nozzle part side turning flow generator. Thereby, since the flow of the refrigerant flowing into the fixed nozzle portion 20a and the fixed throttle 19 of the ejector 20 can be swirled, the same cycle efficiency improvement effect as in the first embodiment can be obtained.

  Further, by adjusting the pipe diameter φd2 of the first outflow pipe 25c and the pipe diameter φd3 of the second outflow pipe 25d, the amount of refrigerant flowing out to each of the outflow pipes 25c and 25d is appropriately distributed as in the first embodiment. it can.

(Third embodiment)
In the present embodiment, a refrigeration cycle apparatus that employs a swirl flow generation / branching section 26 shown in FIG. 6 with respect to the swirl flow generation / branching section 15 of the first embodiment will be described. Other configurations are the same as those of the first embodiment.

  FIG. 6 is a schematic perspective view of the swirling flow generation branching portion 26. The swirling flow generation branching portion 26 has an inflow pipe 26a (inflow passage) through which a refrigerant flows and a substantially cylindrical shape that swirls the refrigerant inside. The swivel cylinder part 26b, the first outflow pipe 26c (first outflow passage) for allowing the refrigerant to flow out from the swivel cylinder part 26b to the fixed throttle 19 side, and the refrigerant outflow from the swirl cylinder part 26b to the fixed nozzle part 20a side of the ejector 20 And a second outflow pipe 26d (second outflow passage).

  The swivel cylinder part 26b is arranged so that the axial direction is in the vertical direction, the inflow pipe 26a is connected to one end of the swivel cylinder part 26b, and further along the outer circumferential tangent direction of the swivel cylinder part 26b. Connected. That is, the inflow pipe 26a is configured to allow the refrigerant to flow in the circumferential direction of the swivel cylinder portion 26b.

  Each outflow pipe 26c, 26d is connected to the end of the swivel cylinder part 26b opposite to the side to which the inflow pipe 26a is connected. Furthermore, the axial direction of each outflow pipe 26c, 26d and the axial direction of the inflow pipe 26a are in different directions. That is, the outflow pipes 26c and 26d are configured to cause the refrigerant to flow out in a direction different from the inflow direction of the refrigerant flowing from the inflow pipe 26a into the swivel tube portion 26b.

  Accordingly, the refrigerant that has flowed into the swivel cylinder part 26b from the inflow pipe 26a swirls along the inner wall of the swirl cylinder part 26b, and as shown by the thick arrows B and C in FIG. , 26d.

  That is, in this embodiment, the branch part Z is formed in the inside of the turning cylinder part 26b, and the turning cylinder part 26b serves as the function of a throttle side turning flow generator and a nozzle part side turning flow generator. Thereby, since the flow of the refrigerant flowing into the fixed nozzle portion 20a and the fixed throttle 19 of the ejector 20 can be swirled, the same effect as the second embodiment can be obtained.

(Fourth embodiment)
In the first to third embodiments described above, an example in which the swirl flow generation branching portions 15, 25, and 26 in which the nozzle portion side swirl flow generator, the throttle side swirl flow generator, and the branch portion Z are integrally configured has been described. However, in the present embodiment, an example will be described in which the nozzle side swirl flow generator, the throttle side swirl flow generator, and the branch part Z are configured separately.

  Specifically, in the refrigeration cycle apparatus of the first embodiment, a three-way joint having one refrigerant inlet and two refrigerant outlets on the downstream side of the expansion valve 14 by eliminating the swirl flow generation branching portion 15. Connected.

  Further, one refrigerant outlet of the three-way joint is connected to the fixed nozzle portion 20 a of the ejector 20, and the other refrigerant outlet is connected to the fixed throttle 19. Then, a swirling flow generator 27 is provided between the three-way joint and the fixed nozzle portion 20a and between the three-way joint and the fixed restrictor 19 to swirl the refrigerant flowing into the decompression portion.

  Accordingly, the branch portion Z is constituted by the three-way joint, and the swirl flow generator 27 constitutes the nozzle portion side swirl flow generator and the throttle side swirl flow generator. That is, the swirl flow generator 27 and the fixed nozzle 20a, and the swirl flow generator 27 and the fixed throttle 19 realize the same configuration as the decompression device of the first feature of the present invention. Other overall configurations are the same as those of the first embodiment.

  As shown in the schematic perspective portion of FIG. 7, the swirling flow generator 27 includes an inflow pipe 27 a (inflow passage) through which the refrigerant flows, a substantially cylindrical swirling tube section 27 b that swirls the refrigerant inside, It has an outflow pipe 27c (outflow passage) through which the refrigerant flows out from the swivel cylinder portion 27b to the fixed nozzle portion 20a side or the fixed throttle 19 side.

  The inflow pipe 27a is connected to one end of the swivel cylinder part 27b, and is further connected along the outer circumferential tangent direction of the swivel cylinder part 27b. That is, the inflow pipe 27a is configured to allow the refrigerant to flow in the circumferential direction of the swivel cylinder portion 27b.

  Outflow pipe 27c is connected to an end portion on the opposite side of the end portion of swivel cylinder portion 27b to the side to which inflow piping 27a is connected. Furthermore, the axial direction of the outflow pipe 27c and the axial direction of the inflow pipe 27a are directed in different directions. That is, the outflow pipe 27c allows the refrigerant to flow out in a direction different from the inflow direction of the refrigerant flowing into the swivel cylinder portion 27b from the inflow pipe 27a.

  Accordingly, the refrigerant that has flowed into the swivel cylinder part 27b from the inflow pipe 27a swirls along the inner wall of the swirl cylinder part 27b, and flows out of the outflow pipe 27c in a swung state, as indicated by a thick arrow D in FIG. . Thereby, since the flow of the refrigerant flowing into the fixed nozzle portion 20a and the fixed throttle 19 of the ejector 20 can be swirled, the same effect as in the first embodiment can be obtained.

(Fifth embodiment)
In the present embodiment, a refrigeration cycle apparatus that employs a swirling flow generator 28 shown in FIG. 8 with respect to the swirling flow generator 27 of the fourth embodiment will be described. Other configurations are the same as those of the fourth embodiment.

  FIG. 8 is a schematic perspective view of the swirling flow generator 28. The swirling flow generator 28 has a refrigerant pipe 28a (refrigerant passage) through which refrigerant flows in and out, and an inner wall surface of the refrigerant pipe 28a has a refrigerant pipe 28a. A spiral groove 28b is formed. Specifically, the spiral groove 28b is formed by twisting the tubular refrigerant pipe 28a. Of course, this spiral groove may be formed by tapping or the like.

  In the swirl flow generator 28, the refrigerant flowing into the swirl swirls along the spiral groove 28b formed on the inner wall surface as indicated by a thick arrow D, and the fixed nozzle portion 20a and the fixed restrictor 19 of the ejector 20 are swung. The flow of the refrigerant flowing into the can be swirled. As a result, the same effect as in the fourth embodiment can be obtained.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows.

  (1) In the above-described embodiment, a capillary tube is employed as the fixed throttle 19, but an orifice, a Laval nozzle, a tapered nozzle, or the like may be employed. Here, FIG. 9 shows the effect of improving the pressure reduction efficiency ηn (nozzle efficiency) when the above-described diaphragm means is adopted as the fixed diaphragm 19. As shown in FIG. 9, the pressure reduction efficiency ηn can be improved regardless of which throttling means is employed.

  (2) Since the refrigeration cycle apparatus 10 of the above-described embodiment is composed of an ejector-type refrigeration cycle apparatus, the refrigeration cycle apparatus 10 includes two nozzle parts 20 a and a fixed throttle 19, and pressure reducing parts. Furthermore, although the configuration of the decompression device having the first characteristic is realized by both the decompression units, the configuration of the decompression device having the first feature may be implemented by any one decompression unit.

  As described above, the cycle efficiency of the ejector-type refrigeration cycle apparatus can be improved even if the configuration of the decompression device having the first characteristic is realized by any one decompression unit. Furthermore, in this case, the swirl flow generators 27 and 28 described in the fourth and fifth embodiments may be arranged upstream of any one of the decompression units.

  (3) In the above-described embodiment, an ejector refrigeration cycle apparatus is employed as the refrigeration cycle apparatus 10, but a normal vapor compression refrigeration cycle apparatus including a compressor, a radiator, a decompression device, and an evaporator is used. Even if the present invention is applied, the cycle efficiency can be improved. Furthermore, in this case, the swirl flow generators 27 and 28 described in the fourth and fifth embodiments may be arranged upstream of the decompressor.

  (4) In the fifth embodiment described above, the spiral flow generator 28 is formed by forming the spiral groove 28b on the inner wall surface of the refrigerant pipe 28a, but the groove is formed in the passage inside the refrigerant pipe 28a. A spiral rectifying plate or the like that performs the same function as 28b may be arranged.

  (5) In the above-described embodiment, the refrigeration cycle apparatus employing the expansion valve 14 and the accumulator 22 has been described. However, as the expansion valve 14, the temperature at which the degree of superheat of the refrigerant on the downstream side of the outflow evaporator 21 is adjusted to a predetermined value. A type expansion valve may be employed. In this case, the accumulator 22 may be eliminated.

  (6) In the above-described embodiment, the outflow side evaporator 21 and the suction side evaporator 23 are joined to each other by brazing joint, but the outflow side evaporator 21 and the suction side evaporator 23 are connected by other methods. It may be integrated. For example, the fins of the outflow side evaporator 21 and the suction side evaporator 23 having a fin-and-tube structure may be shared and divided by a tube configuration in contact with the fins.

  (7) In the first embodiment described above, the axial directions of the first outflow pipe 17 and the second outflow pipe 18 of the swirl flow generation branching section 15 are oriented in a direction perpendicular to the axial direction of the inflow pipe 16. , May be directed in other directions. For example, the axial direction of the first outflow pipe 17 and the second outflow pipe 18 may be directed in a symmetric direction that is divergent.

  (8) In the above-described embodiment, the same air-conditioning target space is cooled by the outflow side evaporator 21 and the suction side evaporator 23, but different air conditioning target spaces are provided by the outflow side evaporator 21 and the suction side evaporator 23. You may make it cool. For example, the suction side evaporator 23 having a low refrigerant evaporation pressure (refrigerant evaporation temperature) is applied to the freezing compartment cooling and the first evaporator 16 is applied to the vehicle interior cooling with respect to the outflow side evaporator 21. Good.

  (9) In each of the above-described embodiments, an example in which a chlorofluorocarbon refrigerant is employed as the refrigerant has been described. However, an HC refrigerant and carbon dioxide may be employed. When carbon dioxide is used as the refrigerant and a supercritical refrigeration cycle apparatus in which the high-pressure side refrigerant pressure exceeds the critical pressure of the refrigerant is configured, the refrigerant is not condensed by the radiator 12, and therefore the receiver 12a may be eliminated. . Furthermore, even in this case, the refrigerant may be decompressed to the gas-liquid two-phase state by the expansion valve 14.

  (10) In the above-described embodiment, the radiator 12 is an outdoor heat exchanger that exchanges heat between the refrigerant and the outside air, and the outflow side evaporator 21 and the suction side evaporator 23 are indoor side heat exchangers for cooling the vehicle interior. However, the outflow side evaporator 21 and the suction side evaporator 23 are configured as outdoor heat exchangers that absorb heat from a heat source such as outside air, and the radiator 12 is heated fluid such as air or water. You may apply this invention to the heat pump cycle comprised as an indoor side heat exchanger which heats.

It is a whole lineblock diagram of the refrigerating cycle device of a 1st embodiment. It is a perspective view of the swirl flow generation | occurrence | production branch part of 1st Embodiment. It is AA sectional drawing of FIG. It is a Mollier diagram which shows the state of the refrigerant | coolant of 1st Embodiment. It is a perspective view of the swirl | flow flow generation | occurrence | production branch part of 2nd Embodiment. It is a perspective view of the swirl | flow flow generation | occurrence | production branch part of 3rd Embodiment. It is a perspective view of the swirl flow generator of 4th Embodiment. It is a perspective view of the swirl flow generator of 5th Embodiment. It is a graph which shows the improvement effect of pressure reduction efficiency (eta) n by the kind of aperture means.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 ... Compressor, 12 ... Radiator, 15, 25, 26 ... Swirling flow generation | occurrence | production branch part,
16, 25a, 26a, 27a ... inflow piping, 17, 25c, 26c ... first outflow piping,
18, 25d, 26d ... second outflow pipe, 19 ... fixed throttle, 20 ... ejector,
20a ... fixed nozzle part, 20b ... refrigerant suction port, 20d ... diffuser part,
21 ... Outflow side evaporator, 23 ... Suction side evaporator, 25b, 26b, 27b ... Swivel cylinder part,
27, 28 ... swirl flow generator, 27c ... outflow pipe, 28a ... refrigerant pipe, 28b ... groove.

Claims (11)

A decompression device applied to a refrigeration cycle device,
A decompression section (19, 20a) for decompressing and expanding the refrigerant;
A swirl flow generating section (15, 25, 26, 27, 28) disposed upstream of the decompression section (19, 20a) and swirling the flow of the refrigerant flowing into the decompression section (19, 20a); Prepared,
The decompression device (19, 20a) is constituted by a fixed throttle, and a decompression device. The swirl flow generating section (15, 25, 26, 27) includes an inflow passage (16, 25a, 26a, 27a) through which a refrigerant flows and a refrigerant flow from the inflow passage (16, 25a, 26a, 27a). The decompression device according to claim 1, further comprising an outflow passage (17, 18, 25c, 25d, 26c, 26d, 27c) for allowing the refrigerant to flow out in a direction different from the inflow direction. The swirl flow generating portion (25, 27) has a cylindrical swirl tube portion (25b, 27b) for swirling the refrigerant inside,
The inflow passages (25a, 27a) allow the refrigerant to flow in the circumferential direction of the swivel tube portions (25b, 27b),
The decompression device according to claim 2, wherein the outflow passage (25c, 25d, 27c) is configured to allow the refrigerant to flow out in an axial direction of the swivel tube portion (25b, 27b). The swirling flow generating section (28) has a refrigerant passage (28a) for flowing in and out the refrigerant,
The decompression device according to claim 1, wherein a spiral groove (28b) is formed on an inner wall surface of the refrigerant passage (28a). A refrigeration cycle apparatus comprising the decompression device according to any one of claims 1 to 4. A compressor (11) for compressing and discharging the refrigerant;
A radiator (12) for radiating the high-temperature and high-pressure refrigerant discharged from the compressor (11);
A branch part (Z) for branching the flow of the refrigerant on the radiator (12) outlet side,
The refrigerant is sucked from the refrigerant suction port (20b) by the high-speed refrigerant flow injected from the fixed nozzle part (20a) for decompressing and expanding one of the refrigerants branched at the branch part (Z), and the high-speed refrigerant flow And an ejector (20) that mixes the refrigerant sucked from the refrigerant suction port (20b) and pressurizes the refrigerant by the diffuser part (20c);
A fixed throttle (19) for decompressing and expanding the other refrigerant branched at the branch (Z);
A suction side evaporator (23) that evaporates the downstream side refrigerant of the fixed throttle (19) and flows out upstream of the refrigerant suction port (20b);
Nozzle part side swirl flow generators (16, 18,) arranged on the downstream side of the branch part (Z) and upstream of the fixed nozzle part (20a) to swirl the flow of the refrigerant flowing into the fixed nozzle part (20a). 25b, 26b, 27b, 28), and throttle side swirl that swirls the flow of the refrigerant that is arranged downstream of the branch part (Z) and upstream of the fixed throttle (19) and flows into the fixed throttle (19). A refrigeration cycle apparatus comprising at least one of flow generators (16, 17, 25b, 26b, 27b, 28). The refrigeration cycle apparatus according to claim 6, further comprising an outflow side evaporator (21) for evaporating the ejected refrigerant (20). The nozzle unit side swirl flow generator (16, 18, 25b, 26b, 27b, 28) and the throttle side swirl flow generator (16, 17, 25b, 26b, 27b, 28) are provided. The refrigeration cycle apparatus according to claim 6 or 7. The nozzle side swirl flow generator (16, 18, 25b, 26b), the throttle side swirl flow generator (16, 17, 25b, 26b) and the branch part (Z) are swirl flow generation branch parts (15 25, 26), the refrigeration cycle apparatus according to claim 8, wherein the refrigeration cycle apparatus is integrally formed. The swirl flow generation branching portion (15, 25, 26) is a first inflowing refrigerant from the inflow passage (16, 25a, 26a) for inflowing the refrigerant and the first inflowing from the inflow passage (16, 25a, 26a). An outflow passage (17, 25c, 26c), and a second outflow passage (18, 25d, 26d) that branches out from the inflow passage (16, 25a, 26a) and flows out the refrigerant,
The first outflow passage (17, 25c, 26c) and the second outflow passage (18, 25d, 26d) allow the refrigerant to flow in a direction different from the inflow direction of the refrigerant flowing into the inflow passage (16, 25a, 26a). The refrigeration cycle apparatus according to claim 9, wherein the refrigeration cycle apparatus is configured to flow out. The axial directions of the inflow passage (16), the first outflow passage (17) and the second outflow passage (18) are arranged on the same horizontal plane,
The passage diameter (φd2) of the first outflow passage (17) and the passage diameter (φd3) of the second outflow passage (18) are formed larger than the passage diameter (φd1) of the inflow passage (16). The refrigeration cycle apparatus according to claim 10.

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