JP2007040612A - Vapor compression type cycle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vapor compression type cycle capable of saving the space for an ejector and a refrigerant distribution part. <P>SOLUTION: This vapor compression type cycle comprises a compressor 11; a radiator 13; the ejector 14 having a nozzle part 14a decompressing and expanding refrigerant on the downstream side of the radiator 13, a refrigerant suction port 14b to the inside of which the refrigerant is sucked by a high-speed refrigerant flow injected from the nozzle part 14a, and a mixing part 14c mixing the high-speed refrigerant flow with the refrigerant sucked by the refrigerant suction port 14b; and an evaporator 15 carrying the refrigerant flowing out of the ejector 14 to a plurality of internal refrigerant passages 15a to evaporate it. A refrigerant distribution device 19 having pressure-raising function of converting speed energy of the mixed refrigerant to pressure energy to raise the pressure thereof, and distributing the mixed refrigerant to the plurality of refrigerant passages 15a of the evaporator 15 is connected to the mixed refrigerant outflow side of the mixing part 14c. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a vapor compression cycle using an ejector serving as a refrigerant decompression means and a refrigerant circulation means. For example, a home air conditioner, a vehicle air conditioner, or a vehicle-mounted luggage is frozen and refrigerated. It is effective when applied to a vehicle refrigeration system.

  Conventionally, as a vapor compression refrigeration cycle using an ejector, for example, one disclosed in Patent Document 1 is known. That is, in this refrigeration cycle, a refrigerant compressor, a refrigerant condenser, an ejector, a first refrigerant evaporator, and a gas-liquid separator are connected in an annular shape by a refrigerant pipe, and the liquid-phase refrigerant side of the gas-liquid separator and the suction of the ejector Are connected to each other by a bypass pipe provided with a second refrigerant evaporator.

The first refrigerant evaporator has a plurality of tubes (paths), and a refrigerant distributor (a distributor in Patent Document 1) is provided between the ejector and the first refrigerant evaporator. The refrigerant distribution unit distributes the gas-liquid two-phase refrigerant flowing out of the ejector equally to each of the plurality of tubes of the first refrigerant evaporator. The ejector, the refrigerant distributor, the first and second refrigerant evaporators, and the gas-liquid separator are integrally formed.
Japanese Patent No. 3265649

  However, the ejector is formed such that the nozzle and the diffuser are arranged in series in the refrigerant flow direction, and further, the refrigerant distributor is disposed on the downstream side of the refrigerant flow of the ejector. There was a problem that it became long in the flow direction and required a large mounting space.

  In view of the above problems, an object of the present invention is to provide a vapor compression cycle that enables space saving of an ejector and a refrigerant distributor.

  In order to achieve the above object, the present invention employs the following technical means.

  In the invention according to claim 1, in the vapor compression cycle, a compressor (11) that sucks and compresses the refrigerant, a radiator (13) that radiates high-pressure refrigerant discharged from the compressor (11), A radiator (13), a nozzle part (14a) for decompressing and expanding the refrigerant on the downstream side, a refrigerant suction port (14b) through which the refrigerant is sucked by a high-speed refrigerant flow injected from the nozzle part (14a), and a high speed An ejector (14) having a mixing section (14c) for mixing the refrigerant flow and the suction refrigerant at the refrigerant suction port (14b), and the refrigerant flowed from the ejector (14) into a plurality of refrigerant flow paths (15a) inside An evaporator (15) that flows and evaporates, and has a pressure-increasing function for increasing the pressure by converting the velocity energy of the mixed refrigerant into pressure energy on the mixed refrigerant outflow side of the mixing section (14c). 15) It is characterized by connecting a refrigerant distributor (19) for distributing the mixed refrigerant in the refrigerant passage number (15a).

  Thereby, in the thing which needs the refrigerant | coolant distribution function to an evaporator (15), the pressure | voltage rise part normally provided in the mixed refrigerant outflow side of the mixing part (14c) of an ejector (14) is abolished, and a refrigerant | coolant distribution apparatus ( 19), the ejector (14) can be downsized. Therefore, it is possible to save the space for the ejector (14) and the refrigerant distributor (19). And since the pressure | voltage rise function in a refrigerant | coolant distribution apparatus (19) can be determined by the total flow-path cross-sectional area of the distribution flow path (19b) for distributing a refrigerant | coolant, without receiving restrictions of the length setting in a refrigerant | coolant flow direction, A desired boosting amount can be provided. In addition, as a matter of course, it can be made inexpensive because the booster can be eliminated.

  The invention according to claim 1 has a refrigerant branch passage (16) branched from the upstream portion of the ejector (14) to reach the refrigerant suction port (14b) as in the invention according to claim 2, The present invention is suitably applied to a structure in which a throttle mechanism (17) is provided in the branch passage (16) and another evaporator (18) is provided on the downstream side of the throttle mechanism (17).

  That is, in the case where two evaporators (15, 18) are set, the refrigerant branched from the upstream portion of the ejector (14) can be decompressed by the throttle mechanism (17) and supplied to the other evaporator (18). It is not necessary to set a gas-liquid separator on the downstream side of the refrigerant flow of the evaporator (15). Moreover, it is because the refrigerant | coolant flow rate to another evaporator (18) can be adjusted independently by the throttle mechanism (17).

  The invention according to claim 3 is characterized in that, in the invention according to claim 2, another throttle mechanism (17a) is provided between the radiator (13) and the ejector (14). .

  Thereby, when the pressure reduction in the ejector (14) is insufficient, the pressure reduction assistance can be performed by the other throttle mechanism (17a).

  In the invention according to claim 4, with respect to the vapor compression cycle according to claim 1, the refrigerant flowing out from the ejector (14) is supplied to the plurality of refrigerant tubes (15 c) via the header tank (15 b). An apparatus including an evaporator (15A) for flowing and evaporating is characterized in that the mixed refrigerant outflow side of the mixing section (14c) of the ejector (14) is connected to the header tank (15b).

  Accordingly, since the header tank (15b) serves to distribute the plurality of refrigerant tubes (15c), the booster of the ejector (14) is eliminated as in the invention described in claim 1 above. can do.

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

(First embodiment)
1 and 2 show a first embodiment of the present invention. FIG. 1 shows an example in which a vapor compression cycle 10 according to the first embodiment is applied to a vehicle refrigeration cycle apparatus. FIG. 2 is a cross-sectional view showing the ejector 14 and the refrigerant distributor 19. In the vapor compression cycle 10 of the present embodiment, a compressor 11 that sucks and compresses refrigerant is rotationally driven by a vehicle travel engine (not shown) via an electromagnetic clutch 12 and a belt.

  The compressor 11 may be a variable capacity type compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or a fixed capacity type that adjusts the refrigerant discharge capacity by changing the operating rate of the compressor operation by switching the electromagnetic clutch 12. Any of the compressors may be used. 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 13 is disposed on the refrigerant discharge side of the compressor 11. The radiator 13 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).

Here, when a normal Freon refrigerant is used as the refrigerant of the vapor compression cycle 10, since the high pressure is a subcritical cycle in which the critical pressure is not exceeded, the radiator 13 acts as a condenser for condensing the refrigerant. . On the other hand, when a refrigerant whose high pressure exceeds a critical pressure, such as carbon dioxide (CO ₂ ), is used as the refrigerant, the vapor compression cycle 10 becomes a supercritical cycle. Does not condense.

  An ejector 14 is disposed further downstream of the refrigerant flow than the radiator 13. The ejector 14 is a decompression means for decompressing the refrigerant, and is also a refrigerant circulation means (momentum transporting pump) that circulates the refrigerant (fluid transport) by suction action (contraction action) of the refrigerant flow ejected at high speed (JIS). Z 8126 number 2.1.2.3 etc.).

  The ejector 14 is arranged in the same space as the nozzle portion 14a for reducing the passage area of the high-pressure refrigerant flowing from the radiator 13 to a small pressure and expanding the high-pressure refrigerant in an isentropic manner, and the refrigerant outlet of the nozzle portion 14a. A refrigerant suction port 14b for sucking a gas-phase refrigerant from the second evaporator 18 described later is provided. Furthermore, a mixing unit 14c that mixes the high-speed refrigerant flow from the nozzle unit 14a and the suction refrigerant from the refrigerant suction port 14b is provided at the downstream side of the refrigerant flow of the nozzle unit 14a and the refrigerant suction port 14b.

  As a feature of the present embodiment, the refrigerant flow downstream of the mixing unit 14c of the ejector 14 has a function of boosting the mixed refrigerant and a plurality of refrigerant channels 15a of the first evaporator 15 described later. A refrigerant distribution device 19 that distributes the refrigerant to is connected.

  The refrigerant distribution device 19 is formed, for example, by providing a plurality of distribution channels 19b inside a cylindrical body 19a. The distribution flow path 19b branches into a plurality from the position corresponding to the refrigerant outflow side of the mixing portion 14c, and extends so as to expand toward the first evaporator 15 side of the main body portion 19a, and opens at the tip end side. ing. Each distribution channel 19b is connected to each refrigerant channel 15a of the first evaporator 15. And the total flow path cross-sectional area which becomes the front end side of the some distribution flow path 19b is set so that it may become the predetermined area larger than the flow path cross-sectional area of the mixing part 14c, and the refrigerant | coolant distribution apparatus 19 is 1st. In addition to the refrigerant distribution function for the evaporator 15, it also has the function of increasing the refrigerant pressure by decelerating the flow of the mixed refrigerant from the mixing section 14c (pressure increasing function), that is, the function of converting the velocity energy of the refrigerant into pressure energy. ing.

  A first evaporator 15 (corresponding to the evaporator in the present invention) 15 is connected to the refrigerant flow downstream side of the refrigerant distributor 19, and the refrigerant flow downstream side of the first evaporator 15 is connected to the suction side of the compressor 11. . The first evaporator 15 has a plurality of refrigerant flow paths (a plurality of paths) 15a therein, and the refrigerant distributed by the refrigerant distribution device 19 flows through the respective refrigerant flow paths 15a. Yes.

  On the other hand, a refrigerant branch passage 16 is branched from an upstream portion of the ejector 14 (an intermediate portion between the radiator 13 and the ejector 14), and a downstream side of the refrigerant branch passage 16 is connected to a refrigerant suction port 14b of the ejector 14. . Z indicates a branch point of the refrigerant branch passage 16.

  A throttle mechanism 17 is disposed in the refrigerant branch passage 16, and a second evaporator (corresponding to another evaporator in the present invention) 18 is disposed at a downstream side of the refrigerant flow from the throttle mechanism 17. The throttling mechanism 17 is a pressure reducing means that adjusts the flow rate of the refrigerant to the second evaporator 18, and can be specifically configured with a fixed throttling such as an orifice. An electric control valve whose valve opening (passage opening) can be adjusted by an electric actuator may be used as the throttle mechanism 17.

  In this embodiment, the two evaporators 15 and 18 are accommodated in one air conditioning case (not shown). Then, air (cooled air) is blown as indicated by an arrow A by an electric blower (not shown) common to the air passage configured in the air conditioning case, and the blown air is cooled by the two evaporators 15 and 18. It is like that.

  The cold air cooled by the two evaporators 15 and 18 is sent to the common cooling target space, and thereby the common cooling target space is cooled by the two evaporators 15 and 18. Here, of the two evaporators 15 and 18, the first evaporator 15 connected to the main flow path on the downstream side of the ejector 14 is disposed on the upstream side of the air flow A, and is connected to the refrigerant suction port 14 b of the ejector 14. The second evaporator 18 is disposed downstream of the air flow A.

  In addition, when applying the vapor compression cycle 10 of this embodiment to the refrigeration cycle apparatus for vehicle air conditioning, the vehicle interior space becomes the space to be cooled. In addition, when the vapor compression cycle 10 of the present embodiment is applied to a refrigeration cycle apparatus for a refrigeration vehicle, the space inside the refrigeration refrigerator of the refrigeration vehicle is a space to be cooled.

  Next, the operation of the first embodiment will be described. When the compressor 11 is driven by the vehicle engine, the high-temperature and high-pressure refrigerant compressed and discharged by the compressor 11 flows into the radiator 13. In the radiator 13, the high-temperature refrigerant is cooled and condensed by the outside air. The high-pressure liquid-phase refrigerant that has flowed out of the radiator 13 is divided into a refrigerant flow toward the ejector 14 and a refrigerant flow toward the branch refrigerant passage 16 at the branch point Z.

  The refrigerant flow flowing into the ejector 14 is decompressed and expanded by the nozzle portion 14a. Therefore, the pressure energy of the refrigerant is converted into velocity energy at the nozzle portion 14a, and the refrigerant is ejected at a high velocity from the outlet of the nozzle portion 14a. Due to the refrigerant pressure drop at this time, the refrigerant (gas phase refrigerant) after passing through the second evaporator 18 in the branch refrigerant passage 16 is sucked from the refrigerant suction port 14b.

  The refrigerant ejected from the nozzle portion 14a and the refrigerant sucked into the refrigerant suction port 14b are mixed in the mixing portion 14c on the downstream side of the nozzle portion 14a and flow into the refrigerant distribution device 19. In the refrigerant distributor 19, the refrigerant mixed in the mixing unit 14 c is distributed to the plurality of distribution channels 19 b, and the velocity (expansion) energy of the refrigerant is changed to pressure energy by expanding the channel cross-sectional area with respect to the mixing unit 14 c. Therefore, the pressure of the refrigerant rises.

  Then, the refrigerant that has flowed out of the refrigerant distributor 19 flows into the first evaporator 15. The first evaporator 15 absorbs heat from the blown air in the direction of arrow A in FIG. 1 and evaporates while the low-temperature low-pressure refrigerant flows through the plurality of refrigerant flow paths 19a. The blown air is cooled by the latent heat of vaporization when the refrigerant evaporates. The vapor phase refrigerant after evaporation is sucked into the compressor 11 and compressed again.

  On the other hand, the refrigerant flow flowing into the branch refrigerant passage 16 is decompressed by the throttle mechanism 17 to become a low-pressure refrigerant, and this low-pressure refrigerant flows into the second evaporator 18. In the second evaporator 18, while the refrigerant flows through the inside, the refrigerant absorbs heat from the blown air in the direction of arrow A in FIG. 1 and evaporates. The blown air is further cooled by the latent heat of evaporation when the refrigerant evaporates. The vapor-phase refrigerant after evaporation is sucked into the ejector 14 from the refrigerant suction port 14b.

  As described above, according to the present embodiment, the refrigerant on the downstream side of the refrigerant distributor 19 can be supplied to the first evaporator 15 and the refrigerant on the branch passage 16 side can also be supplied to the second evaporator 18 through the throttle mechanism 17. Therefore, the first and second evaporators 15 and 18 can exhibit a cooling action simultaneously. Therefore, the cooling target space can be cooled (cooled) by blowing the cool air cooled by both the first and second evaporators 15 and 18 to the cooling target space.

  At that time, the refrigerant evaporation pressure of the first evaporator 15 is the pressure after the pressure is increased by the refrigerant distributor 19, while the outlet side of the second evaporator 18 is connected to the refrigerant suction port 14 b of the ejector 14. Therefore, the lowest pressure immediately after the pressure reduction at the nozzle portion 14 a can be applied to the second evaporator 18.

  Thereby, the refrigerant evaporation pressure (refrigerant evaporation temperature) of the second evaporator 18 can be made lower than the refrigerant evaporation pressure (refrigerant evaporation temperature) of the first evaporator 15. And since the 1st evaporator 15 with a high refrigerant | coolant evaporation temperature is arrange | positioned in the upstream with respect to the flow direction A of blowing air, and the 2nd evaporator 18 with a low refrigerant | coolant evaporation temperature is arrange | positioned in the downstream, the 1st Both the temperature difference between the refrigerant evaporation temperature and the blown air in the evaporator 15 and the temperature difference between the refrigerant evaporation temperature and the blown air in the second evaporator 18 can be ensured.

  For this reason, both the cooling performance of the 1st, 2nd evaporators 15 and 18 can be exhibited effectively. Therefore, the cooling performance for the common space to be cooled can be effectively improved by the combination of the first and second evaporators 15 and 18. Further, the suction pressure of the compressor 11 is increased by the pressure increasing action in the refrigerant distributor 19, and the driving power of the compressor 11 can be reduced.

  In the vapor compression cycle 10 of the present embodiment, the refrigerant branch passage 16 branched from the branch point Z upstream of the ejector 14 is connected to the refrigerant suction port 14b of the ejector 14, and the throttle mechanism 17 is connected to the refrigerant branch passage 16. Since the second evaporator 18 is provided, the low-pressure gas-liquid two-phase refrigerant can be independently supplied to the second evaporator 18 through the refrigerant branch passage 16. For this reason, it is not necessary to set a gas-liquid separator like patent document 1 (FIG. 1 in patent document 1) in the refrigerant | coolant flow downstream of the 1st evaporator 15. FIG.

In the case of a supercritical cycle in which a gas-liquid separator is set as in Patent Document 1 and a refrigerant whose cycle high pressure exceeds the critical pressure is used as a refrigerant, such as CO ₂ refrigerant, cycle operation is performed at a high outside air temperature. When stopped, not only the high pressure side but also the low pressure side becomes supercritical.

  As a result, since the gas-liquid separator cannot perform gas-liquid separation when the cycle operation is restarted, the supercritical high-temperature refrigerant in the gas-liquid separator directly flows into the second evaporator 18 on the refrigerant suction side. The cooling performance of the second evaporator 18 is significantly reduced. On the other hand, according to the present embodiment, the high-pressure refrigerant is branched at the upstream portion of the ejector 14, and the branch refrigerant is decompressed by the throttle mechanism 17 so that the low-temperature refrigerant flows into the second evaporator 18 on the refrigerant suction side. As a result, the cooling performance of the second evaporator 18 can be quickly exhibited even when the cycle operation is restarted.

  Further, even in a subcritical cycle using a normal chlorofluorocarbon refrigerant (a cycle in which the high pressure does not exceed the critical pressure), under a condition where the cycle heat load is small, the difference between the high and low pressures of the cycle is small, and the input of the ejector 14 is small. Become. In this case, in the cycle of Patent Document 1, since the flow rate of the refrigerant passing through the second evaporator 18 depends only on the refrigerant suction capability of the ejector 14, the input reduction of the ejector 14 → the reduction of the refrigerant suction capability of the ejector 14 → the second The refrigerant flow rate of the second evaporator 18 decreases, and it is difficult to ensure the cooling performance of the second evaporator 18.

  On the other hand, according to the present embodiment, the high-pressure refrigerant is branched at the upstream portion of the ejector 14, and the branched refrigerant is sucked into the refrigerant suction port 14 b through the refrigerant branch passage 16. Parallel connection relationship.

  For this reason, the refrigerant can be supplied to the refrigerant branch passage 16 by utilizing not only the refrigerant suction capability of the ejector 14 but also the refrigerant suction / discharge capability of the compressor 11. Thereby, even if the phenomenon that the input of the ejector 14 decreases and the refrigerant suction capacity of the ejector 14 decreases occurs, the degree of decrease in the refrigerant flow rate on the second evaporator 18 side can be made smaller than the cycle of Patent Document 1. Therefore, it is easy to ensure the cooling performance of the second evaporator 18 even under low heat load conditions.

  In addition, the refrigerant flow rate on the second evaporator 18 side can be adjusted independently by the throttle mechanism 17 without depending on the function of the ejector 14, and the refrigerant flow rate to the first evaporator 15 is equal to the refrigerant discharge capacity of the compressor 11. It can be adjusted by the control and the aperture characteristic of the ejector 14. For this reason, the refrigerant | coolant flow volume to the 1st, 2nd evaporators 15 and 18 can be easily adjusted corresponding to each heat load.

  Further, in the present embodiment, since the refrigerant distributor 19 having a pressure increasing function is connected to the mixing portion 14c of the ejector 14, the ejector that requires the refrigerant distribution function to the first evaporator 15 is used. Thus, the pressure increasing unit that is normally provided on the mixed refrigerant outflow side of the mixing unit 14c of the fourteenth unit can be abolished so that it can also be used as the refrigerant distribution device 19, and the ejector 14 can be downsized. Therefore, it is possible to save the space for the ejector 14 and the refrigerant distributor 19.

  The pressure increasing function in the refrigerant distribution device 19 can be determined by the total flow path cross-sectional area of the distribution flow path 19b for distributing the refrigerant, so that the desired pressure increase amount can be obtained without being restricted by the length setting in the refrigerant flow direction. Can be given. In addition, as a matter of course, it can be made inexpensive because the booster can be eliminated.

(Second Embodiment)
A second embodiment of the present invention is shown in FIG. The second embodiment is different from the first embodiment in that the first throttle is between the radiator 13 and the ejector 14, more specifically, between the radiator 13 and the branch point Z of the refrigerant branch passage 16. A mechanism (corresponding to another throttle mechanism in the present invention) 17a is provided, and the throttle mechanism on the refrigerant upstream side of the second evaporator 18 is a second throttle mechanism 17b.

  The first throttle mechanism 17a is a temperature expansion valve whose opening degree is variable according to the refrigerant temperature on the refrigerant outlet side of the first evaporator 15, and the second throttle mechanism 17b is a fixed throttle.

  Thereby, when the decompression at the ejector 14 is insufficient, the first throttling mechanism 17a can assist the decompression, and the superheat degree on the refrigerant outlet side in the first evaporator 15 can be maintained to be a predetermined superheat degree. .

  As a modification of the second embodiment, as shown in FIG. 4, a first throttle mechanism 17a is disposed between the branch point Z of the refrigerant branch flow path 16 and the ejector 14, and the second throttle mechanism 17c. It is good also as a temperature type expansion valve by which the opening degree of itself is varied according to the refrigerant | coolant temperature of the refrigerant | coolant exit side of the 2nd evaporator 18.

  Thus, even if the cycle heat load fluctuates, the degree of superheat on the refrigerant outlet side in the first evaporator 15 and the second evaporator 18 is maintained at a predetermined superheat degree by the respective throttle mechanisms 17a and 17c. However, the refrigerant flow rates of the respective evaporators 15 and 18 can be controlled.

(Third embodiment)
A third embodiment of the present invention is shown in FIGS. The third embodiment is different from the first embodiment in that a first evaporator (corresponding to the evaporator of the present invention) 15A includes a plurality of stacked refrigerant tubes 15c, and the longitudinal direction of each refrigerant tube 15b. The end is connected to the header tank 15b.

  Here, the mixed refrigerant outflow side of the mixing portion 14c of the ejector 14 is connected to the header 15b of the first evaporator 15A. As shown in FIGS. 5 and 6, the connection direction of the ejector 14 with respect to the header tank 15b can be variously adapted, for example, along the longitudinal direction of the header tank 15b or across the longitudinal direction of the header tank 15b.

  Thereby, since the header tank 15b performs the distribution function with respect to the some refrigerant | coolant tube 15c, the pressure | voltage rise part of the ejector 14 can be abolished similarly to the said 1st Embodiment.

(Other embodiments)
The ejector 14 and the refrigerant distributor 19 of the present invention are compared with the first to third embodiments in the cycle shown in Patent Document 1 (FIG. 1 in Patent Document 1), that is, the first evaporator 15 and the compression. A gas-liquid separator is provided between the compressor 11 and the gas-liquid separator, and the refrigerant suction port 14b of the ejector 14 is applied to a cycle connected by a bypass passage in which the second evaporator 18 is disposed. Also good.

It is a schematic diagram which shows the vapor | steam compression-type cycle in 1st Embodiment. It is sectional drawing which shows the ejector and refrigerant | coolant distribution apparatus in FIG. It is a schematic diagram which shows the vapor compression type cycle in 2nd Embodiment. It is a schematic diagram which shows the vapor | steam compression-type cycle in the modification of 2nd Embodiment. It is an external appearance perspective view which shows the ejector and 1st evaporator in 1 of 3rd Embodiment. It is an external appearance perspective view which shows the ejector and 1st evaporator in 2 of 3rd Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Vapor compression cycle 11 Compressor 13 Radiator 14 Ejector 14a Nozzle part 14b Refrigerant suction port 14c Mixing part 15, 15A 1st evaporator (evaporator)
15a Refrigerant flow path (multiple refrigerant flow paths)
15b Header tank 15c Refrigerant tube 16 Refrigerant branch passage 17 Throttle mechanism 17a First throttling mechanism (another throttling mechanism)
18 Second evaporator (another evaporator)
19 Refrigerant distributor

Claims (4)

A compressor (11) for sucking and compressing refrigerant;
A radiator (13) for radiating heat of the high-pressure refrigerant discharged from the compressor (11);
A nozzle part (14a) for decompressing and expanding the refrigerant on the downstream side of the radiator (13), a refrigerant suction port (14b) through which the refrigerant is sucked by a high-speed refrigerant flow injected from the nozzle part (14a), and An ejector (14) having a mixing section (14c) for mixing the high-speed refrigerant flow and the suction refrigerant of the refrigerant suction port (14b);
An evaporator (15) that evaporates the refrigerant that has flowed out of the ejector (14) through a plurality of refrigerant flow paths (15a) inside;
On the outflow side of the mixed refrigerant in the mixing section (14c), there is a pressure increasing function for increasing pressure by converting the velocity energy of the mixed refrigerant into pressure energy, and a plurality of refrigerant flow paths (15a) of the evaporator (15) A vapor compression cycle, characterized in that a refrigerant distribution device (19) for distributing the mixed refrigerant is connected to the vapor compression cycle. A refrigerant branch passage (16) branched from an upstream portion of the ejector (14) and reaching the refrigerant suction port (14b);
The throttle mechanism (17) is provided in the refrigerant branch passage (16), and another evaporator (18) is provided downstream of the throttle mechanism (17). Vapor compression cycle.   The vapor compression cycle according to claim 2, wherein another throttle mechanism (17a) is provided between the radiator (13) and the ejector (14). A compressor (11) for sucking and compressing refrigerant;
A radiator (13) for radiating heat of the high-pressure refrigerant discharged from the compressor (11);
A nozzle part (14a) for decompressing and expanding the refrigerant on the downstream side of the radiator (13), a refrigerant suction port (14b) through which the refrigerant is sucked by a high-speed refrigerant flow injected from the nozzle part (14a), and An ejector (14) having a mixing section (14c) for mixing the high-speed refrigerant flow and the suction refrigerant of the refrigerant suction port (14b);
An evaporator (15A) for flowing and evaporating the refrigerant flowing out of the ejector (14) through the header tank (15b) to the plurality of refrigerant tubes (15c);
A vapor compression cycle, wherein the mixed refrigerant outflow side of the mixing section (14c) is connected to the header tank (15b).

Images