JP2008051397A - Ejector type refrigerating cycle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve the cooling performance of an evaporator without deteriorating loading capacity and cost. <P>SOLUTION: This ejector type refrigerating cycle includes: a compressor 11; a radiator 13; an ejector 14; a first evaporator 15 for evaporating coolant flowing out of the ejector 14 to exhibit cooling capacity; a branch passage 16 for dividing a coolant on the outlet side of the radiator at an inlet side of the ejector 14 and guiding the same to a coolant suction port 14b; a capillary tube 17 disposed in the branch passage 16 and forming a throttle mechanism for reducing the pressure of the coolant at the outlet side of the radiator 13; and a second evaporator 18 disposed at an outlet side of the throttle mechanism 17 to evaporate the coolant and exhibit the cooling capability, wherein the first evaporator 15 has a tank 15b for distributing and collecting a coolant flow to the plurality of tubes 21, and the capillary tube 17 is disposed in the tank 15b so that a coolant flowing through the capillary tube 17 and a coolant flowing through a space part located in an outlet part for the coolant flow in the tank 15b make heat exchange. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an ejector-type refrigeration cycle having an ejector that serves as a refrigerant decompression unit and a refrigerant circulation unit. For example, the present invention relates to a vehicle air-conditioning device or a vehicle refrigeration device that freezes and refrigerates in-vehicle luggage. It is effective to apply.

  Conventionally, this type of ejector-type refrigeration cycle is known from Patent Document 1 and the like. In this Patent Document 1, a first evaporator is disposed on an outlet side of an ejector that serves as a refrigerant pressure reducing unit and a refrigerant circulating unit, and the outlet side of the first evaporator is connected to a suction side of a compressor. Disclosed is an ejector-type refrigeration cycle in which a refrigerant branch passage branching from an upstream portion of the refrigerant is provided, a second evaporator is disposed downstream of the refrigerant branch passage, and an outlet side of the second evaporator is connected to a refrigerant suction port of the ejector. Has been.

  According to the ejector-type refrigeration cycle of Patent Document 1, the pressure drop generated by the high-speed flow of the refrigerant at the time of expansion is used to suck the gas-phase refrigerant discharged from the second evaporator and the refrigerant at the time of expansion. Since the speed energy is converted into pressure energy by the diffuser part (pressure raising part) of the ejector and the refrigerant pressure is increased, the driving power of the compressor can be reduced. For this reason, the operating efficiency of the cycle can be improved.

  In the ejector refrigeration cycle disclosed in Patent Document 1, the first and second evaporators are integrally configured to improve the efficiency of the mounting work when the ejector refrigeration cycle is mounted on an application target such as a vehicle. ing.

  Further, in the ejector type refrigeration cycle of Patent Document 1, a pressure reducing means (fixed throttle) is disposed in the refrigerant branch passage, and the refrigerant flow rate to the second evaporator is adjusted by the pressure reducing means (fixed throttle). ing.

  On the other hand, the present applicant previously described in Japanese Patent Application No. 2005-105992 (hereinafter referred to as the prior application example) between the low pressure refrigerant on the compressor suction side and the high pressure refrigerant flowing on the second evaporator side. Has proposed an ejector-type refrigeration cycle with an internal heat exchanger for heat exchange.

According to the ejector-type refrigeration cycle of the prior application example, the high-pressure refrigerant flowing to the second evaporator side is cooled by exchanging heat with the low-pressure refrigerant on the compressor suction side, so that the enthalpy of the refrigerant at the inlet of the second evaporator is reduced. The enthalpy difference between the second evaporator inlet and outlet can be enlarged. For this reason, the cooling performance of the second evaporator can be improved.
JP 2005-308384 A

  However, in the prior application example, there is a problem that the mountability of the ejector refrigeration cycle is deteriorated by newly providing an internal heat exchanger. In addition, there is a problem in that the number of parts of the ejector refrigeration cycle increases, resulting in high costs.

  In view of the above points, an object of the present invention is to improve the cooling performance of an evaporator without deteriorating mountability and cost.

To achieve the above object, the present invention includes a compressor (11) for sucking and compressing refrigerant,
A radiator (13) that radiates heat of the high-pressure refrigerant discharged from the compressor (11);
A nozzle (14a) that decompresses and expands the refrigerant on the outlet side of the radiator (13), a refrigerant suction port (14b) through which the refrigerant is sucked by a jet refrigerant flow injected from the nozzle portion (14a), and a jet refrigerant flow An ejector (14) having a booster (14d) for converting the velocity energy of the refrigerant flow mixed with the refrigerant sucked from the refrigerant suction port (14b) into pressure energy;
A first evaporator (15) that evaporates the refrigerant that has flowed out of the ejector (14) and exhibits cooling capacity;
A branch passage (16) for branching the refrigerant on the outlet side of the radiator (13) on the inlet side of the ejector (14) and leading to the refrigerant suction port (14b);
A capillary tube (17) disposed in the branch passage (16) and serving as a throttle mechanism for decompressing the refrigerant on the outlet side of the radiator (13);
A branch passage (16), which is disposed on the outlet side of the capillary tube (17) and has a second evaporator (18) which evaporates the refrigerant and exerts a cooling capacity;
The first evaporator (15) has a plurality of tubes (21) through which refrigerant flows, and a tank (15b) that distributes or collects refrigerant flows to the plurality of tubes (21).
The capillary tube (17) is connected to the tank (15b) so that the refrigerant flowing in the capillary tube (17) and the refrigerant flowing in the space (39) located at the outlet of the refrigerant flow in the tank (15b) exchange heat. ) Is a first feature.

  According to this, the refrigerant flowing in the capillary tube (17) and the refrigerant flowing in the space (39) located at the outlet of the refrigerant flow in the tank (15b) of the first evaporator (15) exchange heat. Therefore, the intermediate pressure refrigerant flowing in the capillary tube (17) is cooled by exchanging heat with the low pressure refrigerant flowing in the space (39).

  For this reason, since the enthalpy of the second evaporator inlet refrigerant can be reduced and the enthalpy difference between the second evaporator inlet and outlet can be expanded, the cooling performance of the second evaporator (18) can be improved.

  That is, since the capillary tube (17) and the tank (15b) of the first evaporator (15) can play the same role as the internal heat exchanger in the above-mentioned prior application example, the internal heat exchanger is separately provided. There is no need to provide.

  Furthermore, since the capillary tube (17) is disposed in the tank (15b) of the first evaporator (15), the capillary tube (17) is integrated with the tank (15b) of the first evaporator (15). . For this reason, mountability can be improved compared with the case where a capillary tube (17) is comprised separately from the tank (15b) of a 1st evaporator (15).

  As a result, the cooling performance of the second evaporator (15) can be improved without deteriorating the mountability and cost.

In the present invention, specifically, the capillary tube (17) is disposed outside the tank (15b),
The outer surface of the capillary tube (17) is in contact with the outer surface of the space (39) in the tank (15b).

  Thus, the refrigerant flowing in the capillary tube (17) and the refrigerant flowing in the space (39) are heated with a simple configuration in which the capillary tube (17) is integrally brazed to the outer surface side of the tank (15b). Can be exchanged.

In the present invention, specifically, the capillary tube (17) is disposed in the space (39) of the tank (15b),
The outer surface of the capillary tube (17) is in direct contact with the refrigerant flowing through the space (39).

  According to this, since the outer surface of the capillary tube (17) is in direct contact with the refrigerant flowing through the space (39), it is compared with the case where the outer surface of the capillary tube (17) is in contact with the outer surface of the tank (15b). Thus, the thermal resistance between the refrigerant flowing through the capillary tube (17) and the refrigerant flowing through the space (39) can be reduced.

  For this reason, since heat exchange between the refrigerant flowing through the capillary tube (17) and the refrigerant flowing through the space (39) can be promoted, the cooling performance of the second evaporator (18) can be further improved.

  Further, since the capillary tube (17) is disposed inside the tank (15b) and the outer surface of the capillary tube (17) is in direct contact with the refrigerant flowing through the space (39), the capillary tube (17) is placed on the outer surface of the capillary tube (17). The pressure of the refrigerant flowing through the space (39) acts. Therefore, the pressure difference between the inside and outside of the capillary tube (17) becomes the pressure difference between the refrigerant flowing through the capillary tube (17) and the refrigerant flowing through the space (39).

  For this reason, when the capillary tube (17) is arranged outside the tank (15b), that is, a refrigerant in which the pressure difference between the inside and outside of the capillary tube (17) flows inside the capillary tube (17) and the outside of the capillary tube (17). Compared with the case of a pressure difference with air (atmospheric pressure), the pressure difference between the inside and outside of the capillary tube (17) can be reduced.

  For this reason, compared with the case where the capillary tube (17) is disposed outside the tank (15b), the pressure resistance of the capillary tube (17) can be reduced, so that the plate thickness of the capillary tube (17) can be reduced. The thermal resistance between the refrigerant flowing through the capillary tube (17) and the refrigerant flowing through the space (39) can be further reduced.

  As a result, heat exchange between the refrigerant flowing through the capillary tube (17) and the refrigerant flowing through the space (39) can be further promoted, so that the cooling performance of the second evaporator (18) can be further improved.

  In the present invention, more specifically, since the capillary tube (17) is integrally brazed with the tank (15b), the operation of integrating the capillary tube (17) with the tank (15b) is efficiently performed. be able to.

The present invention also includes a compressor (11) that sucks and compresses refrigerant,
A radiator (13) that radiates heat of the high-pressure refrigerant discharged from the compressor (11);
A nozzle (14a) that decompresses and expands the refrigerant on the outlet side of the radiator (13), a refrigerant suction port (14b) through which the refrigerant is sucked by a jet refrigerant flow injected from the nozzle portion (14a), and a jet refrigerant flow An ejector (14) having a booster (14d) for converting the velocity energy of the refrigerant flow mixed with the refrigerant sucked from the refrigerant suction port (14b) into pressure energy;
A branch passage (16) for branching the refrigerant on the outlet side of the radiator (13) on the inlet side of the ejector (14) and leading to the refrigerant suction port (14b);
A capillary tube (17) disposed in the branch passage (16) and serving as a throttle mechanism for decompressing the refrigerant on the outlet side of the radiator (13);
An evaporator (18) disposed on the outlet side of the capillary tube (17) in the branch passage (16) and evaporating the refrigerant to exhibit cooling capacity;
The evaporator (18) has a plurality of tubes (21) through which the refrigerant flows, and a tank (18b) that distributes or collects the refrigerant flow to the plurality of tubes (21).
The capillary tube (17) is connected to the tank (18b) so that the refrigerant flowing in the capillary tube (17) and the refrigerant flowing in the space (32) located at the outlet of the refrigerant flow in the tank (18b) exchange heat. ) Is a second feature.

  According to this, the refrigerant flowing in the capillary tube (17) and the refrigerant flowing in the space (32) located at the outlet of the refrigerant flow in the tank (18b) of the evaporator (18) exchange heat. The intermediate pressure refrigerant flowing through the capillary tube (17) is cooled by exchanging heat with the low pressure refrigerant flowing through the space (32).

  For this reason, since the enthalpy of the evaporator inlet refrigerant can be reduced and the enthalpy difference between the evaporator inlet and outlet can be enlarged, the cooling performance of the evaporator can be improved.

  That is, since the capillary tube (17) and the tank (18b) of the evaporator (18) can play the same role as the internal heat exchanger in the above-mentioned prior application example, a separate internal heat exchanger is provided. There is no need.

  Furthermore, since the capillary tube (17) is disposed in the tank (18b) of the evaporator (18), the capillary tube (17) is integrated with the tank (18b) of the evaporator (18). For this reason, mountability can be improved compared with the case where a capillary tube (17) is comprised separately from the tank (18b) of an evaporator (18).

  As a result, the cooling performance of the evaporator (18) can be improved without deteriorating the mountability and cost.

  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)
Hereinafter, an ejector refrigeration cycle according to a first embodiment of the present invention will be described. FIG. 1 shows an example in which an ejector refrigeration cycle 10 according to a first embodiment is applied to a refrigeration cycle apparatus for a vehicle. In the ejector refrigeration cycle 10 of this embodiment, a compressor 11 that sucks and compresses refrigerant is rotationally driven by a vehicle travel engine (not shown) via an electromagnetic clutch 11a, a belt, and the like.

  As the compressor 11, a variable capacity 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 intermittently connecting the electromagnetic clutch 11a. 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 12 is disposed on the refrigerant discharge side of the compressor 11. The radiator 12 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, as a refrigerant of the ejector refrigeration cycle 10, in this embodiment, a refrigerant whose high pressure does not exceed the critical pressure, such as a refrigerant of chlorofluorocarbon and HC, is used to constitute a vapor compression subcritical cycle. ing. For this reason, the radiator 12 acts as a condenser that condenses the refrigerant.

  A liquid receiver 12 a is provided on the outlet side of the radiator 12. As is well known, the liquid receiver 12a has a vertically long tank shape, and constitutes a gas-liquid separator that separates the gas-liquid refrigerant and accumulates excess liquid refrigerant in the cycle. At the outlet of the liquid receiver 12a, liquid refrigerant is led out from the lower side inside the tank shape. In addition, the liquid receiver 12a is provided integrally with the heat radiator 12 in this example.

  Further, as the radiator 12, a heat exchanger for condensation located on the upstream side of the refrigerant flow, a liquid receiver 12a for introducing the refrigerant from the heat exchanger for condensation and separating the gas and liquid of the refrigerant, and the liquid receiver A known configuration having a supercooling heat exchanging section for supercooling the saturated liquid refrigerant from the vessel 12a may be employed.

  A temperature type expansion valve 13 is disposed on the outlet side of the liquid receiver 12a. The temperature type expansion valve 13 is a pressure reducing means for reducing the pressure of the liquid refrigerant from the liquid receiver 12 a and has a temperature sensing part 13 a disposed in the suction side passage of the compressor 11.

  As is well known, the temperature type expansion valve 13 detects the degree of superheat of the compressor suction side refrigerant based on the temperature and pressure of the suction side refrigerant (evaporator outlet side refrigerant described later) of the compressor 11 and sucks the compressor. The valve opening (refrigerant flow rate) is adjusted so that the degree of superheat of the side refrigerant becomes a predetermined value set in advance.

  An ejector 14 is disposed on the outlet side of the temperature type expansion valve 13. The ejector 14 is a pressure reducing means for reducing the pressure of the refrigerant, and is also a refrigerant circulating means (momentum transport type pump) for fluid transportation for circulating the refrigerant by suction action (contraction action) of the refrigerant flow ejected at high speed.

  In the ejector 14, the passage area of the refrigerant (intermediate pressure refrigerant) after passing through the expansion valve 13 is narrowed down, and the nozzle part 14a for further decompressing and expanding the refrigerant is disposed in the same space as the refrigerant outlet of the nozzle part 14a. A refrigerant suction port 14b for sucking a gas-phase refrigerant from the second evaporator 18 described later is provided.

  Furthermore, a mixing portion 14c that mixes the high-speed refrigerant flow from the nozzle portion 14a and the suction refrigerant of the refrigerant suction port 14b is provided in the refrigerant flow downstream portion of the nozzle portion 14a and the refrigerant suction port 14b.

  And the diffuser part 14d which makes a pressure | voltage rise part is arrange | positioned in the refrigerant | coolant flow downstream of the mixing part 14c. The diffuser portion 14d is formed in a shape that gradually increases the passage area of the refrigerant, and serves to increase the refrigerant pressure by decelerating the refrigerant flow, that is, to convert the velocity energy of the refrigerant into pressure energy.

  The first evaporator 15 is connected to the outlet side of the diffuser portion 14 d of the ejector 14, and the outlet side of the first evaporator 15 is connected to the suction side of the compressor 11.

  On the other hand, a refrigerant branch passage 16 is branched from the inlet side of the ejector 14 (an intermediate portion between the outlet side of the temperature type expansion valve 13 and the inlet side of the ejector 14), and the downstream side of the refrigerant branch passage 16 is connected to the ejector 14. It is connected to the refrigerant suction port 14b. Z indicates a branch point of the refrigerant branch passage 16.

  A throttle mechanism 17 is arranged in the refrigerant branch passage 16, and a second evaporator 18 is arranged downstream of the refrigerant flow from the throttle mechanism 17. The throttle mechanism 17 is a pressure reducing means for adjusting the flow rate of the refrigerant to the second evaporator 18, and is specifically constituted by a capillary tube which is a fixed throttle.

  In the present embodiment, the two evaporators 15 and 18 are assembled into an integral structure with the configuration described later. The two evaporators 15 and 18 are accommodated in a case (not shown), and air (cooled air) is blown as indicated by an arrow A by an electric blower 19 common to the air passage configured in the case. The blown air is cooled by the two evaporators 15 and 18.

  The cool air cooled by the two evaporators 15 and 18 is sent to a common cooling target space (not shown), whereby the two cooling units 15 and 18 cool the common cooling target space. Yes. 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 arranged on the upstream side (windward side) of the air flow A, and the refrigerant suction port of the ejector 14 is arranged. The second evaporator 18 connected to 14b is arranged on the downstream side (leeward side) of the air flow A.

  Note that, when the ejector refrigeration cycle 10 of the present embodiment is applied to a vehicle air conditioning refrigeration cycle apparatus, the interior space of the vehicle is a space to be cooled. Further, when the ejector refrigeration 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.

  By the way, in this embodiment, the ejector 14, the first and second evaporators 15 and 18, and the throttle mechanism 17 are assembled as one integrated unit 20. Next, a specific example of the integrated unit 20 will be described.

  FIG. 2 is an exploded perspective view of the integrated unit 20, and FIG. 3 is a schematic perspective view showing a refrigerant flow path configuration of the integrated unit 20. In this example, the two evaporators 15 and 18 are completely integrated as one evaporator structure. Therefore, the first evaporator 15 constitutes an upstream region of the air flow A in one evaporator structure, and the second evaporator 18 constitutes a downstream region of the air flow A in one evaporator structure. It is supposed to be.

  The basic configurations of the first evaporator 15 and the second evaporator 18 are the same, and the heat exchange core portions 15a and 18a and the tank portions 15b and 15c located on both upper and lower sides of the heat exchange core portions 15a and 18a, respectively. 18b and 18c.

  Here, each of the heat exchange core portions 15a and 18a includes a plurality of tubes 21 extending in the vertical direction. Between the plurality of tubes 21, a passage through which the heat exchange medium, in this embodiment, air to be cooled passes is formed. The fins 22 can be disposed between the plurality of tubes 21 so that the tubes 21 and the fins 22 can be joined.

  The heat exchange core portions 15 a and 18 a have a laminated structure of tubes 21 and fins 22. The tubes 21 and the fins 22 are alternately stacked in the left-right direction of the heat exchange core portions 15a and 18a. In other embodiments, a configuration without the fins 22 can be employed.

  2 and 3, only a part of the laminated structure of the tube 21 and the fin 22 is shown, but the laminated structure of the tube 21 and the fin 22 is configured over the entire area of the heat exchange core portions 15a and 18a. The air blown by the electric blower 19 passes through the gap portion of the laminated structure.

  The tube 21 constitutes a refrigerant passage, and is formed of a flat tube whose cross-sectional shape is flat along the air flow direction A. The fin 22 is a corrugated fin obtained by bending a thin plate material into a wave shape, and is joined to the flat outer surface side of the tube 21 to expand the air-side heat transfer area.

  The tube 21 of the heat exchange core portion 15a and the tube 21 of the heat exchange core portion 18a constitute independent refrigerant passages, and tank portions 15b and 15c on both upper and lower sides of the first evaporator 15 and upper and lower portions of the second evaporator 18 are arranged. The tank portions 18b and 18c on both sides constitute mutually independent refrigerant passage spaces.

  Here, the tank portions 15 b and 15 c of the first evaporator 15 and the tank portions 18 b and 18 c of the second evaporator 18 are both elongated in the arrangement direction of the plurality of tubes 21. The arrangement direction of the tubes 21 is the left-right direction in FIGS. 2 and 3, and is a direction orthogonal to the air flow direction A.

  The tank portions 15b, 15c on both the upper and lower sides of the first evaporator 15 have tube fitting hole portions (not shown) into which the upper and lower end portions of the tube 21 of the heat exchange core portion 15a are inserted and joined. The upper and lower end portions of the upper and lower ends communicate with the internal spaces of the tank portions 15b and 15c.

  Similarly, the tank portions 18b and 18c on both the upper and lower sides of the second evaporator 18 have tube fitting holes (not shown) into which the upper and lower ends of the tube 21 of the heat exchange core portion 18a are inserted and joined. The upper and lower end portions of the tube 21 communicate with the internal spaces of the tank portions 18b and 18c.

  As a result, the tank portions 15b, 15c, 18b, and 18c on the upper and lower sides distribute the refrigerant flow to the plurality of tubes 21 of the corresponding heat exchange core portions 15a and 18a, respectively, or collect the refrigerant flows from the plurality of tubes 21. To play a role.

  4 is a cross-sectional view of the main part on the side of the connection block 23 shown in FIGS. 2 and 3 in the upper tank part of the evaporator, and FIG. 6 is an enlarged cross-sectional view taken along line BB in FIG.

  In this example, the two upper tanks 15b and 18b are divided into a tube side (bottom side) half-cracked member 24 and an anti-tube side (top side) half-cracked member 25 extending in the tank longitudinal direction (tube arrangement direction), By combining these two half-breaking members 24 and 25 and joining them together, two cylindrical shapes extending in the tank longitudinal direction (tube arrangement direction) are formed side by side in the air flow direction A. The two cylindrical side surfaces in the longitudinal direction (right end in FIG. 5) are closed with a cap 26. Thus, two upper tanks 15b and 18b are formed.

  The tube-side half-cracked member 24 has a substantially W-shaped cross-sectional shape in which the tube-side half-cracked portions of the two upper tanks 15b and 18b are integrally formed. Each of the tanks 15b and 18b has a substantially M-shaped cross-sectional shape formed by integrally molding the anti-tube side half cracks of the tanks 15b and 18b.

  Although not shown, the two lower tanks 15c and 18c are also configured by a tube-side half-cracked member, an anti-tube-side half-cracked member, and a cap, like the two upper tanks 15b and 18b.

  In addition, as a concrete material of the evaporator components such as the tube 21, the fin 22, the tank portions 15 b, 15 c, 18 b, 18 c, aluminum which is a metal excellent in thermal conductivity and brazing property is suitable. By forming each part with an aluminum material, the entire configuration of the first and second evaporators 15 and 18 can be assembled by integral brazing.

  In this embodiment, the capillary tube and the refrigerant passage connection block 23 constituting the throttle mechanism 17 shown in FIGS. 2 and 3 are also assembled integrally with the first and second evaporators 15 and 18 by brazing. Yes.

  On the other hand, since the ejector 14 forms a highly accurate minute passage in the nozzle portion 14a, when the ejector 14 is brazed, the nozzle is formed at a high temperature during brazing (a brazing temperature of aluminum: around 600 ° C.). The part 14a is thermally deformed, resulting in a problem that the passage shape, dimensions, and the like of the nozzle part 14a cannot be maintained as originally designed.

  Therefore, the ejector 14 is assembled to the evaporator side after the first and second evaporators 15 and 18, the capillary tube 17 and the connection block 23 are integrally brazed.

  Next, the assembly structure of the ejector 14, the capillary tube 17 and the connection block 23 will be described more specifically.

  The capillary tube 17 and the connection block 23 are formed of an aluminum material in the same manner as the evaporator parts. The capillary tube 17 is placed on a valley-shaped portion formed at the center of the substantially M-shaped cross section of the anti-tube-side half crack member 25 of the two upper tanks 15b and 18b, and the outer surface of the capillary tube 17 is the upper side. The upper tanks 15b and 18b are integrally brazed while being in contact with the outer surfaces of the tanks 15b and 18b.

  As shown in FIG. 5, the outlet side end portion (right end portion) of the capillary tube 17 is bent into a U shape and inserted into the through hole 26a of the cap 26 that closes the other side surface in the longitudinal direction of the upper tank 18b. It opens into the right space 27 of the upper tank 18b. The outer peripheral surface of the capillary tube 17 and the through hole 26a of the cap 26 are sealed and joined by brazing.

  As shown in FIG. 2, the connection block 23 is a member that is brazed and fixed to one side surface in the longitudinal direction of the upper tanks 15 b and 18 b of the first and second evaporators 15 and 18 with the intervening plate 28 interposed therebetween. Thus, one refrigerant inlet 29 and one refrigerant outlet 30 of the integrated unit 20 shown in FIG.

  Accordingly, the intervening plate 28 is also formed of an aluminum material in the same manner as the evaporator component, the capillary tube 17 and the connection block 23. The intervening plate 28 is a member that plays a role of holding and fixing one end portion in the longitudinal direction of the ejector 14 (one end portion on the nozzle portion 14a side) while constituting a refrigerant passage to be described later in cooperation with the connection block 23.

  As shown in FIGS. 7 and 8, the connection block 23 is provided with one refrigerant inlet 29 and one refrigerant outlet 30 and a dedicated hole 31 for inserting the ejector 14 into the evaporator tank. ing.

  The dedicated hole portion 31 for inserting the ejector is a circular hole, and is open so as to face the side surface portion of the left tank space 32 in the upper tank portion 18 b of the second evaporator 18. Here, the left tank space 32 constitutes a refrigerant assembly side tank space.

  A cylindrical portion 33 concentrically facing the hole portion 31 is formed in the intervening plate 28. As shown in FIGS. 4 and 7, the cylindrical portion 33 protrudes in a cylindrical shape from the flat plate-like substrate portion of the interposition plate 28 into the left tank space 32 of the upper tank portion 18b, and in the inner diameter direction at the protruding tip portion. A flange portion 33a bent in a ring shape is integrally formed.

  The inner diameter of the flange portion 33a is set to be slightly larger than the maximum outer diameter portion of the diffuser portion 14d at the tip portion of the ejector 14, and the tip portion of the ejector 14 is connected to the hole portion 31 of the connection block 23 and the interposed plate. 28 can be inserted into the left tank space 32 of the upper tank portion 18b through the cylindrical portion 33.

  As shown in FIG. 4, in the longitudinal direction of the ejector 14, a groove 14e for mounting the O-ring 34a protrudes in a ring shape radially outward on the outer peripheral surface of the inlet side (nozzle part 14a side) end. The groove 14e is formed and is engaged with the flange 33a at the tip of the cylindrical portion 33 of the intervening plate 28. That is, the insertion position of the ejector 14 can be defined by the engagement between the O-ring groove 14e and the flange 33a of the interposition plate 28.

  The O-ring 34a is elastically pressed against the inner peripheral surface of the cylindrical portion 33, whereby the outer peripheral surface on the inlet side of the ejector 14 can be sealed, and a main passage 29a described later directly communicates with the left tank space 32. To prevent.

  Further, a groove portion 33b (FIG. 7) is formed at one predetermined position in the circumferential direction of the flange portion 33a, and a convex portion (not shown) extending in the longitudinal direction on the outer peripheral surface of the ejector 14 is fitted into the groove portion 33b. By doing so, rotation of the ejector 14 can be prevented and the assembly position of the ejector 14 in the circumferential direction can be defined.

  As shown in FIG. 7 and FIG. 8, a concave groove portion 35 that is bent in a “U” shape is formed on the surface of the connection block 23 on the side of the interposed plate 28, and one end portion of the concave groove portion 35 is formed. The refrigerant inlet 29 communicates. The hole 31 and the cylindrical portion 33 of the intervening plate 28 communicate with the intermediate portion near the other end of the concave groove 35.

  As shown in FIG. 7, the intervening plate 28 is formed with a concave groove portion 36 that opposes the concave groove portion 35 of the connection block 23, and the refrigerant passage cross-sectional area is increased by the combination of the both concave groove portions 35 and 36. The concave shape of the concave groove portion 36 is shown in FIG.

  Of the refrigerant passage formed by the concave groove portion 35 of the connection block 23, the main passage 29a is formed by the passage portion toward the cylindrical portion 33 of the interposed plate 28. Accordingly, the inner opening of the cylindrical portion 33 constitutes a main passage side opening 37 (FIG. 4) communicating with the main passage 29a.

  Of the refrigerant passage formed by the concave groove 35, the branch passage 16 is formed by the passage on the other end 35 a side further than the position facing the cylindrical portion 33. On the other hand, a branch passage side opening 38 opens in a circular shape at a portion of the interposition plate 28 facing the branch passage 16 of the connection block 23 and communicates with the branch passage 16.

  The opening 38 is sealed and joined to the inlet side end portion (left side end portion in FIG. 2) of the capillary tube 17 by brazing.

  In addition, the intervening plate 28 has a refrigerant at a portion facing the side surface portion of the refrigerant outlet 30 of the connection block 23 and the left side space 39 of the upper tank 15b of the first evaporator 15 (a space portion located at the outlet portion of the refrigerant flow) 39. An outlet side opening 40 is opened, and the left space 39 is communicated with the refrigerant outlet 30 through the opening 40.

  By caulking and fixing the plurality of first claw portions 41 protruding from the interposition plate 28 toward the evaporator to the upper tanks 15b and 18b, the interposition plate 28 can be temporarily fixed to the evaporator side before brazing. On the other hand, the plurality of second claw portions 42 protruding from the interposition plate 28 toward the connection block 23 are caulked and fixed to the connection block 23, so that the connection block 23 is temporarily connected to the evaporator side via the interposition plate 28 before brazing. Can be fixed.

  The ejector fixing plate 43 is a member that is disposed at a substantially central portion in the longitudinal direction of the internal space of the upper tank 18b of the second evaporator 18 and is brazed to the inner wall surface of the upper tank 18b. The ejector fixing plate 43 serves to partition the internal space of the upper tank 18b into two spaces in the tank longitudinal direction, that is, the left space 32 and the right space 27.

  As shown in FIGS. 4, 5, and 9, the ejector fixing plate 43 is integrally formed with a cylindrical portion 43a, and the diffuser portion 14d of the ejector 14 is fitted and fixed to the inner peripheral side of the cylindrical portion 43a. The inner space of the upper tank 18b serves to partition the left space 32 and the right space 27. The fitting portion between the cylindrical portion 43a and the diffuser portion 14d is sealed by an O-ring 34b (FIG. 4).

  The claw portion 43b (FIG. 9) protruding upward from the ejector fixing plate 43 passes through the slit-like hole 44 (FIG. 5) on the upper surface of the upper tank 18b and is caulked and fixed to the upper tank 18b. Thereby, the ejector fixing plate 43 can be temporarily fixed to the upper tank 18b before brazing.

  A partition plate 45 is disposed at a substantially central portion in the vertical direction of the right space 27 in the upper tank 18b. As shown in FIG. 11, the partition plate 45 is a generally plate-like member extending in the longitudinal direction of the upper tank 18b, and is brazed to the inner wall surface of the upper tank 18b.

  The right space 27 in the upper tank 18b is further partitioned by the partition plate 45 into two vertical spaces, that is, an upper space 27a and a lower space 27b.

  Of the end portions in the longitudinal direction of the partition plate 45, the end portion on the outlet end side of the capillary tube 17 (the right end portion in FIGS. 5 and 11) is formed with a bent portion 45a bent upward at a right angle. A claw portion 45b protruding upward from the tip portion of the portion 45a is formed. The claw portion 45b passes through a slit-like hole 46 (FIG. 5) on the upper surface of the upper tank 18b and is fixed to the upper tank 18b by caulking.

  Thereby, the partition plate 45 can be temporarily fixed to the upper tank 18b before brazing. Further, by setting a predetermined interval shown in FIG. 5 between the bent portion 45 a of the partition plate 45 and the outlet end portion of the capillary tube 17, the outlet end portion of the capillary tube 17 is located below the right space 27. It communicates with (refrigerant distribution side space) 27b.

  A rib 45c (FIG. 11) protruding in a triangular shape is stamped and formed inside the bent portion 45a of the partition plate 45. Thereby, the rigidity in the bending part 45a of the partition plate 45 is ensured, and the bending angle is prevented from changing.

  Of the end portions in the longitudinal direction of the partition plate 45, an end portion on the ejector fixing plate 43 side (the left end portion in FIGS. 5 and 11) is formed with a bent portion 45d bent downward at a right angle, and this bent portion 45d. Is in contact with the ejector fixing plate 43 and the tube-side half crack member 24 of the upper tank 18b, and is brazed to both of them.

  The front end portion of the ejector 14 in the longitudinal direction (the outlet portion of the diffuser portion 14d) penetrates through the cylindrical portion 43a of the ejector fixing plate 43 and protrudes into the upper space 27a of the right space 27 in the upper tank 18b, and the diffuser portion 14d. The outlet portion directly communicates with the upper space 27a.

  Here, a downward arcuate recess 45e is formed in the partition plate 45 adjacent to the bent part 45d, and the lower part on the outlet side of the diffuser part 14d of the ejector 14 is fitted on the arcuate recess 45e. A guide portion 45f is formed on the partition plate 45 in succession to the arcuate recess 45e. The guide portion 45f has an inclined arc shape and smoothly guides the refrigerant flow flowing out from the outlet portion of the diffuser portion 14d.

  As shown in FIG. 5, a partition plate 47 is disposed at a substantially central portion in the longitudinal direction of the internal space of the upper tank 15 b of the first evaporator 15, and the internal space of the upper tank 15 b is disposed in the longitudinal direction by the partition plate 47. It is partitioned into two spaces, that is, a left space 39 and a right space 48.

  The right space (refrigerant distribution side space) 48 of the upper tank 15b of the first evaporator 15 communicates with the upper space 27a of the right space 27 in the upper tank 18b through a communication hole 49 (FIGS. 5 and 6). Yes. As shown in FIG. 5, a plurality (four in the illustrated example) of the communication holes 49 are formed along the tank longitudinal direction.

  As shown in FIG. 6, the communication hole 49 is formed at a joint between the two upper tanks 15b and 18b. More specifically, the flat plate surface 50 formed at the center of the substantially W-shaped cross section of the tube side half-cracked members 24 of the two upper tanks 15b and 18b, and the opposite tube side of the two upper tanks 15b and 18b. When joining the flat plate surface 51 formed at the center of the substantially M-shaped cross-section of the half-cracked member 25 by brazing, a plurality of upward concave shapes are formed on the flat plate surface 51 of the anti-tube side half-cracked member 25. The communication hole 49 is formed by a space surrounded by the concave shape and the flat plate surface 50 of the tube side half crack member 24.

  FIG. 4 shows that the ejector 14 is inserted into the upper tank 18b through the hole shape (main passage side opening 37) of the ejector insertion hole 31 of the connection block 23 and the cylindrical portion 33 of the interposition plate 28. After the insertion work of the ejector 14 is completed, the spacer 52 is inserted into the ejector insertion hole 31 of the connection block 23, and the male screw 53a on the outer peripheral surface of the cylindrical plug 53 is inserted into the ejector. It is screwed into a female screw on the inner peripheral surface of the hole 31 for use.

  As shown in FIG. 10, the spacer 52 is integrally formed with a protruding piece 52b protruding vertically (in the ejector longitudinal direction) from the ring-shaped main body 52a. The protruding piece 52b is brought into contact with the inlet side end portion (left end portion in FIG. 4) in the longitudinal direction of the ejector 14, thereby fixing the ejector 14 in the longitudinal direction.

  Here, since the protruding piece 52b has a shape protruding from only a part in the circumferential direction of the main body 52a, the protruding piece 52b is located on the side opposite to the refrigerant inlet 29 in the ejector insertion hole 31, as shown in FIG. Therefore, the refrigerant flow between the main passage 29a of the connection block 23 and the main passage side opening 37 inside the cylindrical portion 33 of the interposition plate 28 is not hindered.

  Further, since the main body 52a of the spacer 52 is formed in a ring shape, the spacer 52 can be easily assembled by grasping the peripheral edge of the ring-shaped center hole 52c and inserting it into the hole 31. it can.

  The plug 53 has a hexagonal locking recess 53b (FIGS. 2 and 4) for locking the tool on its outer end surface, and an O-ring 34c is disposed on the outer peripheral surface on the tip side of the male screw 53a. The O-ring 34c is elastically pressed against the inner peripheral surface of the ejector insertion hole 31 of the connection block 23 to seal between the plug 53 and the ejector insertion hole 31.

  On the other hand, as shown in FIGS. 5 and 6, a refrigerant storage plate 55 is disposed at a substantially central portion in the vertical direction of the lower space 27 b of the right space 27 in the upper tank 18 b. The refrigerant storage plate 55 is a member that is brazed to the inner wall surface of the upper tank 18b, and is a plate-like member that extends in the longitudinal direction of the upper tank 18b in a mountain shape as shown in FIG. A plurality of holes 55a punched in a rectangular shape are provided in the longitudinal direction of the upper tank 18b at the top of the mountain-shaped cross section of the refrigerant storage plate 55.

  As shown in FIG. 5, the lower space 27 b constitutes a distribution side tank space that distributes the refrigerant to the upper end openings of the plurality of tubes 21. Therefore, the refrigerant storage plate 55 stores the liquid refrigerant of the gas-liquid two-phase refrigerant from the capillary tube 17 in the valley portions 56 (FIG. 6) formed on both sides of the chevron cross section, and the liquid refrigerant is stored in a plurality of rectangular shapes. The refrigerant is uniformly distributed to the upper end openings of the plurality of tubes 21 by dropping from the shape hole 55a.

  As shown in FIG. 8, in the connection block 23, two screw holes 57 are provided at an intermediate portion between the refrigerant inlet 29 and the refrigerant outlet 30 on the side surface (outer surface) opposite to the tanks 15b and 18b of the evaporators 15 and 18. The refrigeration cycle components, specifically, the temperature type expansion valve 13 and the connection block 23 can be screwed together using the screw hole 57.

  By the way, in this embodiment, since the capillary tube 17, the connection block 23, the interposition plate 28, the ejector fixing plate 43, the partition plate 45, and the refrigerant | coolant storage plate 55 are all components integrally brazed with the evaporators 15 and 18. FIG. In the same manner as the evaporator parts (tube 21, fin 22, tank portions 15b, 15c, 18b, 18c, etc.), it is formed of an aluminum material.

  On the other hand, since the spacer 52 and the plug 53 are parts for assembling the ejector 14 that is assembled after the evaporators 15 and 18 are integrally brazed, it is not necessary to use a material that takes brazing into account. It is not limited. Accordingly, the spacer 52 and the plug 53 can be made of various metals including an aluminum material, and can also be a resin material.

  Further, in the ejector 14, the nozzle portion 14a is made of a material such as stainless steel or brass, and portions other than the nozzle portion 14a (a housing portion forming the refrigerant suction port 14b, a mixing portion 14c, a diffuser portion 14d, etc.) are copper, Although it is made of a metal material such as aluminum, it may be made of a resin (non-metal material).

  The refrigerant flow path of the entire integrated unit 20 configured as described above will be specifically described with reference to FIGS. 3 to 5. The refrigerant inlet 29 of the connection block 23 is branched into the main passage 29 a and the branch passage 16. The refrigerant in the main passage 29a passes through the main passage side opening 37 inside the cylindrical portion 33 of the interposition plate 28, and then passes through the ejector 14 (nozzle portion 14a → mixing portion 14c → diffuser portion 14d) to be decompressed. The subsequent low-pressure refrigerant flows into the upper space 27a of the right space 27 in the upper tank 18b of the second evaporator 18 located on the leeward side.

  Thereafter, the refrigerant flows into the right space 48 of the upper tank 15b of the first evaporator 15 located on the windward side as indicated by an arrow a through a plurality of communication holes 49.

  The refrigerant in the right space 48 is distributed to the plurality of tubes 21 on the right side of the upwind heat exchange core portion 15a, and the plurality of tubes 21 descends as shown by arrows b and flows into the right side in the lower tank 15c. To do. Since no partition plate is provided in the lower tank 15c, the refrigerant moves from the right side of the lower tank 15c to the left side as shown by an arrow c.

  The refrigerant on the left side of the lower tank 15c ascends the plurality of tubes 21 on the left side of the upwind heat exchange core 15a as indicated by the arrow d and flows into the left space 39 of the upper tank 15b. The refrigerant flows to the refrigerant outlet 30 of the connection block 23 as indicated by an arrow e.

  On the other hand, the refrigerant in the branch passage 16 of the connection block 23 first passes through the capillary tube 17 and is depressurized, and the low-pressure refrigerant (gas-liquid two-phase refrigerant) after depressurization is the second evaporator as indicated by the arrow f. It flows into the lower space 27b of the right space 27 of the 18 upper tanks 18b.

  Of the refrigerant that has flowed into the lower space 27b, the liquid refrigerant temporarily accumulates in the troughs 56 (FIG. 6) located on the left and right sides of the chevron shape of the refrigerant storage plate 55, and near the top of the chevron shape of the refrigerant storage plate 55. The liquid refrigerant overflows from the rectangular hole 55a and falls downward.

  The gas-liquid two-phase refrigerant including the liquid refrigerant dropped from the rectangular hole 55a moves down the plurality of tubes 21 on the right side of the leeward side heat exchange core portion 18a as shown by the arrow g and moves to the right side in the lower tank 18c. Flows into the section. Since no partition plate is provided in the lower tank 18c, the refrigerant moves from the right side of the lower tank 18c to the left side as indicated by an arrow h.

  The refrigerant on the left side of the lower tank 18c moves up the plurality of tubes 21 on the left side of the leeward heat exchange core 18a as indicated by an arrow i and flows into the left space 32 of the upper tank 18b. Since the refrigerant suction port 14b of the ejector 14 communicates with the left space 32, the refrigerant in the left space 32 is sucked into the ejector 14 from the refrigerant suction port 14b.

  Since the integrated unit 20 has the above-described refrigerant flow path configuration, only one refrigerant inlet 29 is provided in the connection block 23 as a whole, and one refrigerant outlet 30 is also provided in the connection block 23 as a whole. Just do it.

  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 12. In the radiator 12, the high-temperature refrigerant is cooled and condensed by the outside air. The high-pressure refrigerant that has flowed out of the radiator 12 flows into the liquid receiver 12a, where the gas-liquid refrigerant is separated in the liquid receiver 12a, and the liquid refrigerant is led out from the liquid receiver 12a and passes through the expansion valve 13. .

  In the expansion valve 13, the valve opening degree (refrigerant flow rate) is adjusted so that the degree of superheat of the outlet refrigerant (compressor suction refrigerant) of the first evaporator 15 becomes a predetermined value, and the high-pressure refrigerant is decompressed. The refrigerant (intermediate pressure refrigerant) after passing through the expansion valve 13 flows into one refrigerant inlet 29 provided in the connection block 23 of the integrated unit 20.

  Here, the refrigerant flow is divided into a refrigerant flow from the main passage 29 a of the connection block 23 toward the ejector 14 and a refrigerant flow from the refrigerant branch passage 16 of the connection block 23 toward the capillary tube 17.

  And the refrigerant | coolant flow which flowed into the ejector 14 is decompressed and expanded by the nozzle part 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 diffuser portion 14d. In the diffuser portion 14d, the passage area is enlarged, so that the speed (expansion) energy of the refrigerant is converted into pressure energy, so that the pressure of the refrigerant rises.

  The refrigerant that has flowed out of the diffuser portion 14d of the ejector 14 flows in the refrigerant flow paths indicated by arrows a to e in FIG. During this time, in the heat exchange core portion 15a of the first evaporator 15, the low-temperature low-pressure refrigerant absorbs heat from the blown air in the direction of arrow A and evaporates. The vapor phase refrigerant after evaporation is sucked into the compressor 11 from one refrigerant outlet 30 and compressed again.

  On the other hand, the refrigerant flow that has flowed into the refrigerant branch passage 16 is decompressed by the capillary tube 17 to become a low-pressure refrigerant, and the low-pressure refrigerant flows through the refrigerant flow paths indicated by arrows f to i in FIG. During this time, in the heat exchange core portion 18 a of the second evaporator 18, the low-temperature low-pressure refrigerant absorbs heat from the blown air that has passed through the first evaporator 15 and 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 diffuser portion 14d of the ejector 14 is supplied to the first evaporator 15, and the refrigerant on the branch passage 16 side is supplied to the second evaporator through the capillary tube (throttle mechanism) 17a. 18 can also be supplied to the first and second evaporators 15 and 18, so that the cooling action can be exerted 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 evaporating pressure of the first evaporator 15 is the pressure after being increased by the diffuser portion 14d, and the outlet side of the second evaporator 18 is connected to the refrigerant suction port 14b of the ejector 14. The lowest pressure immediately after the pressure reduction in the nozzle portion 14a 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 It is possible to secure 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.

  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 can be increased by the pressure increasing action in the diffuser portion 14d, and the driving power of the compressor 11 can be reduced.

  Further, the refrigerant flow rate on the second evaporator 18 side can be independently adjusted by the capillary tube (throttle mechanism) 17 without depending on the function of the ejector 14, and the refrigerant flow rate to the first evaporator 15 can be adjusted by the throttle of the ejector 14. It can be adjusted according to the characteristics. 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.

  By the way, under the condition where the cycle heat load is small, the difference between the high and low pressures of the cycle becomes small, the input of the ejector 14 becomes small, and the phenomenon that the refrigerant suction capacity of the ejector 14 is lowered occurs. For this reason, the refrigerant | coolant flow volume of the 2nd evaporator 18 reduces, and there exists a problem that it is difficult to ensure the cooling performance of the 2nd evaporator 18. FIG.

  Therefore, in the present embodiment, the refrigerant that has passed through the expansion valve 13 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 so that the refrigerant branch passage 16 is ejected from the ejector 14. Is connected in parallel.

  As a result, 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. For this reason, even if the phenomenon of a decrease in the input of the ejector 14 → a decrease in the refrigerant suction capability of the ejector 14 occurs under a low heat load condition, the degree of decrease in the refrigerant flow rate on the second evaporator 18 side can be reduced. Therefore, it is easy to ensure the cooling performance of the second evaporator 18 even under low heat load conditions.

  By the way, according to the present embodiment, the ejector 14, the first and second evaporators 15 and 18, and the capillary tube 17 forming the fixed throttle are assembled as one structure, that is, an integrated unit 20, as shown in FIG. As a result, only one refrigerant inlet 29 and one refrigerant outlet 30 are provided for the integrated unit 20 as a whole.

  As a result, when the ejector-type refrigeration cycle 10 is mounted on a vehicle, one refrigerant inlet 29 is connected to the outlet side of the expansion valve 13 as a whole integrated unit 20 including the various components 14, 15, 18, and 17. The pipe connection work can be completed by simply connecting one refrigerant outlet 30 to the suction side of the compressor 11.

  At the same time, since the ejector 14 is configured to be inserted into the evaporator tank 18b, the interior space of the evaporator tank can be effectively used as a mounting space for the ejector 14, and the ejector 14 and the evaporators 15, 18 are integrated. The mounting space for the unit 20 can be reduced.

  Further, since the capillary tube 17 is arranged in the valley-shaped portion formed in the central portion of the substantially M-shaped cross section of the anti-tube-side half crack member 25 in the two upper tanks 15b and 18b, the valley which is a dead space The shape portion can be effectively used as a mounting space for the capillary tube 17, and the mounting space for the integrated unit 20 can be reduced.

  Therefore, the ejector 14, the first evaporator 15, the second evaporator 18, and the capillary tube 17 are configured as independent parts, and each of these parts is independently fixed to a chassis part such as a vehicle body. Compared with a case where separate structures are used in which the pipes are connected to each other, the mounting of the ejector refrigeration cycle 10 having the plurality of evaporators 15 and 18 on the vehicle can be greatly improved. And compared with the case where a separate structure is employ | adopted, a cycle part number can be reduced and cost reduction can be aimed at.

  Furthermore, in the present embodiment, the following cooling performance improvement effect can be exhibited while taking advantage of such mountability on a vehicle and cost. That is, since the outer surface of the capillary tube 17 is in contact with the outer surface of the left space 39 in the upper tank 15 b of the first evaporator 15, the intermediate pressure refrigerant flowing in the capillary tube 17 and the upper tank of the first evaporator 15. Heat exchange with the refrigerant flowing in the left space 39 of 15b is performed.

  For this reason, since the refrigerant passing through the refrigerant branch passage 16 is cooled by the refrigerant flowing in the left space 39 of the upper tank 15b of the first evaporator 15, the refrigerant enthalpy difference between the refrigerant inlet and outlet in the second evaporator 18 (Cooling capacity) can be increased, and the cooling performance of the second evaporator 18 can be improved.

  That is, the capillary tube 17 and the upper tank 15b in this embodiment are the same as the internal heat exchanger (the high-temperature high-pressure refrigerant passing through the refrigerant branch passage and the low-temperature low-pressure refrigerant downstream of the first evaporator) in the above-mentioned prior application example. It plays the same role as an internal heat exchanger that performs heat exchange.

  For this reason, compared with the case where an internal heat exchanger is separately provided as in the above-mentioned prior application example, the cooling performance of the second evaporator 18 is reduced without incurring deterioration in mountability and cost in the vehicle. It can be improved.

  Further, the use of the integrated unit 20 can also exhibit the following incidental effects such as improvement in cooling performance.

  (1) According to the integrated unit 20, the length of the connecting passage between the various parts 14, 15, 18, 17 can be reduced to a small amount, so that the pressure loss of the refrigerant flow path can be reduced and at the same time the low-pressure refrigerant and the surroundings Heat exchange with the atmosphere can be effectively reduced. Thereby, the cooling performance of the 1st, 2nd evaporators 15 and 18 can be improved.

  (2) In particular, in the second evaporator 18, the evaporation pressure of the second evaporator 18 can be reduced by the amount of pressure loss reduction due to the abolition of the connection pipe between the outlet side and the ejector refrigerant suction port 14b. The cooling performance of the two evaporators 18 can be effectively improved without increasing the compressor power.

  That is, since the ejector 14 is inserted into the space 32 where the refrigerant flow is gathered and located at the outlet of the refrigerant flow in the tank of the second evaporator 18, the refrigerant suction port 14 b of the ejector 14 is connected to the space 32. By directly communicating (opening), the refrigerant evaporated by the second evaporator 18 on the leeward side can be directly sucked into the refrigerant suction port 14b.

  For this reason, piping for the refrigerant suction passage to the refrigerant suction port 14b becomes unnecessary, the refrigerant passage configuration can be simplified, and the cooling performance of the second evaporator 18 can be improved by reducing the pressure loss of the suction refrigerant flow. .

  (3) Since the ejector 14 is configured to be inserted into the evaporator tank 18b, the ejector 14 can be disposed in a low-temperature atmosphere in the evaporator tank section, and the heat treatment of the ejector 14 (attaching a heat insulating material) Can be abolished.

  Moreover, since the ejector 14 is inserted into the evaporator tank 18b after the first and second evaporators 15 and 18 are integrally brazed, the dimensional accuracy due to thermal deformation of the ejector nozzle portion 14a due to the high temperature during brazing. Defects such as deterioration can be avoided.

  (4) Since the insertion hole 31 of the ejector 14 is sealed with the screw-type plug 53, the ejector 14 can be easily attached and detached by removing and attaching the plug 53.

  (5) Since the refrigerant inlet 29 and the refrigerant outlet 30 are formed in one connection block 23 and the hole 31 for inserting the ejector 14 is formed, the hole 31 can be formed at low cost.

  (6) Since the groove portion 35 is formed in the one connection block 23 to form the refrigerant passages 25a and 16, the role of the refrigerant passage forming member can be shared by the one connection block 23, thereby reducing the cost. And downsizing can be achieved.

  (7) More specifically, since the refrigerant passages 25a and 16 are formed by combining the connection block 23 and the intervening plate 28, the refrigerant passages 25a and 16 are bent in the shape of a "<" shape illustrated in FIG. Even in a complicated shape such as the shape, the refrigerant passages 25a and 16 can be easily formed by the combination of the members 24 and 44.

  (8) The groove portion 35 of the connection block 23 forms a main refrigerant passage 25 a that connects the refrigerant inlet 29 to the inlet side of the ejector nozzle portion 14 a and a branch passage 16 that connects the refrigerant inlet 29 to the inlet side of the capillary tube 17. And the connection position to the inlet side of the capillary tube 17 in the branch channel | path 16 is made into the downstream of the refrigerant | coolant flow rather than the connection position to the inlet side of the ejector nozzle part 14a in the main refrigerant channel | path 25a.

  According to this, in the refrigerant flow from the refrigerant inlet 29, the liquid refrigerant having a high density and a large inertia force is more likely to flow into the capillary tube 17 inlet side than the inlet side of the ejector nozzle portion 14a. As a result, the refrigerant flow rate control function by the capillary tube 17 can be satisfactorily exhibited.

  (9) The cylindrical portion 33 is formed on the intervening plate 28, and the ejector 14 is fitted and fixed to the cylindrical portion 33. The ejector fixing plate 43 is disposed in the tank 18b, and the cylindrical portion of the ejector fixing plate 43 is provided. The ejector 14 is also fitted and fixed to 43a.

  According to this, two places in the longitudinal direction of the ejector 14 can be fixed to the evaporator tank 18b side, and the ejector 14 can be stably fixed. Moreover, since the cylindrical portion 33 and the cylindrical portion 43a guide the insertion of the ejector when the ejector 14 is inserted, the insertion operation of the elongated ejector 14 can be easily performed.

  Here, the cylindrical portion 33 and the ejector fixing plate 43 of the intervening plate 28 constitute an ejector fixing mechanism located on the same axis as the ejector insertion hole 31. In this embodiment, the ejector fixing mechanism is used as the ejector 14. However, it is also possible to use only one ejector fixing mechanism in the longitudinal direction of the ejector 14.

  (10) Since the groove part 33b is provided in the cylindrical part 33 of the interposition plate 28, and the protrusion part (not shown) by the side of the ejector 14 is fitted to this groove part 33b, rotation of the ejector 14 is prevented. The assembly position can be defined. Thereby, the position of the refrigerant suction port 14b of the ejector 14 can always be fixed at a predetermined suitable position on the refrigerant flow path configuration.

  In the present embodiment, the combination of the groove portion 33b of the cylindrical portion 33 of the interposition plate 28 and the convex portion on the ejector 14 constitutes an anti-rotation means that prescribes the assembly position of the ejector 14 in the circumferential direction. However, the rotation preventing means may be provided not in the fitting portion between the cylindrical portion 33 of the interposition plate 28 and the ejector 14 but in the fitting portion between the cylindrical portion 43 a of the ejector fixing plate 43 and the ejector 14.

  Further, the rotation preventing means may be provided on both the interposed plate 28 side and the ejector fixing plate 43 side.

  (11) Since the hole portion 31 for inserting the ejector 14 is disposed in the side surface portion where the refrigerant inlet 29 is disposed in the side surface portion in the longitudinal direction of the evaporator tank, the refrigerant from the refrigerant inlet 29 has a short passage length. It can be introduced into the ejector nozzle portion 14a. For this reason, the refrigerant from the refrigerant inlet 29 can be introduced into the ejector nozzle portion 14a with a small pressure loss.

  (12) In FIG. 2, the tube 21 within the range of the arrow X passes through the refrigerant outlet side passage (refrigerant passage indicated by the arrow i in FIG. 3) disposed on the left side of the ejector fixing plate 43 and communicating with the left space 32 of the tank 18b. On the other hand, the tube 21 within the range of the arrow Y is arranged on the right side of the ejector fixing plate 43 and is connected to the refrigerant inlet side passage (arrow g in FIG. 3) communicating with the lower space 27b of the right space 27 of the tank 18b. The refrigerant passage). Then, the number of refrigerant outlet side tubes 21 (total passage cross-sectional area) indicated by arrow X communicating with the left space 32 of the tank 18b is set to the refrigerant inlet side tube indicated by arrow Y communicating with the lower space 27b of the right space 27 of the tank 18b. More than 21 (total passage cross-sectional area).

  Thereby, since the longitudinal direction length of the left side space 32 becomes larger than the longitudinal direction length of the right side space 27, the insertion space of the longitudinal direction of the ejector 14 can be expanded, the length of the ejector 14 is increased and the ejector performance is improved. it can.

  Further, the dryness of the refrigerant flowing through the refrigerant outlet side tube 21 indicated by the arrow X is larger than the dryness of the refrigerant flowing through the refrigerant inlet side tube 21 indicated by the arrow Y, and the specific volume of the refrigerant increases as the dryness increases. Since it increases, the pressure loss of the refrigerant flow tends to increase. However, in the present embodiment, as described above, the number of the refrigerant outlet side tubes 21 indicated by the arrow X is larger than the number of the refrigerant inlet side tubes 21 indicated by the arrow Y. The passage sectional area becomes larger than the total passage sectional area of the refrigerant inlet side tube 21 indicated by the arrow Y, and an increase in pressure loss of the refrigerant flow can be avoided.

(Second Embodiment)
In the first embodiment, the outer surface of the capillary tube 17 is in contact with the outer surfaces of the upper tanks 15b, 18b of the first and second evaporators 15, 18, but in the second embodiment, as shown in FIG. Further, the outer surface of the capillary tube 17 is in contact with only the outer surface of the upper tank 15 b of the first evaporator 15.

  FIG. 13 is a cross-sectional view of the evaporator upper tank portion in the air flow direction in the present embodiment, and corresponds to FIG. 6 in the first embodiment. In the present embodiment, a gap 70 is formed between the outer surface of the capillary tube 17 and the outer surface of the upper tank 18 b of the second evaporator 18.

  As a method of forming the gap 70, for example, when the capillary tube 17 is integrally brazed to the upper tank 15b, a gap (not shown) is maintained between the outer surface of the capillary tube 17 and the outer surface of the upper tank 18b of the second evaporator 18. The gap 70 can be formed by holding the tool and removing the gap holder after brazing.

  By the way, in the first embodiment, not only the outer surface of the capillary tube 17 contacts the outer surface of the left space 39 of the upper tank 15b, but also the outer surface of the right space 48 of the upper tank 15b, the outer surface of the left space 32 of the upper tank 18b, The outer surface of the right space 27 of the upper tank 18b is also in contact.

  For this reason, the intermediate pressure refrigerant flowing in the capillary tube 17 not only exchanges heat with only the refrigerant with high dryness (refrigerated refrigerant) flowing in the left space 39 of the upper tank 15b in the upper tanks 15b and 18b, Heat exchange is also performed with a refrigerant having a low dryness (a refrigerant in the middle of evaporation) flowing through the right space 48 of the upper tank 15b, the left space 32 of the upper tank 18b, and the right space 27 of the upper tank 18b.

  As a result, the dryness of the refrigerant flowing through the spaces 48, 32, and 27 increases compared to the case where heat is exchanged only with the refrigerant flowing through the left space 39 of the upper tank 15b. As a result, the amount of heat absorbed from the blown air is reduced in the refrigerant flow path downstream of the refrigerant flow, and the cooling performance of the first and second evaporators 15 and 18 is reduced.

  More specifically, when the dryness of the refrigerant flowing in the right space 48 of the upper tank 15b and the left space 32 of the upper tank 18b increases, the amount of heat absorbed from the blown air in the refrigerant flow paths indicated by arrows b and d in FIG. It will decline. Further, when the dryness of the refrigerant flowing in the right space 27 of the upper tank 18b increases, the amount of heat absorbed from the blown air decreases in the refrigerant flow paths indicated by arrows g, i, b, and d in FIG.

  Therefore, in the present embodiment, since the outer surface of the capillary tube 17 is in contact with only the outer surface of the upper tank 15b of the first evaporator 15, the intermediate pressure refrigerant flowing in the capillary tube 17 is left in the left space 32 and the upper tank 18b. It is possible to avoid heat exchange with a refrigerant having a low dryness flowing in the right space 27. For this reason, compared with the first embodiment, the cooling performance of the first and second evaporators 15 and 18 can be improved.

  In the present embodiment, the outer surface of the capillary tube 17 is in contact with the outer surface of the left space 39 and the outer surface of the right space 48 of the upper tank 15b and is brazed. However, the outer surface of the capillary tube 17 is the upper tank 15b. Only the outer surface of the left space 39 may be brazed.

  In this case, since the contact area between the outer surface of the capillary tube 17 and the outer surface of the right space 48 of the upper tank 15b can be reduced, the dryness of the intermediate pressure refrigerant flowing in the capillary tube 17 flowing in the right space 48 of the upper tank 15b. Heat exchange with a small refrigerant can be suppressed. As a result, the cooling performance of the second evaporator 18 can be further improved.

(Third embodiment)
In the second embodiment, the outer surface of the capillary tube 17 is in contact with the outer surface of the upper tank 15b of the first evaporator 15. However, in the third embodiment, as shown in FIG. 1 is inserted into the upper tank 15b of the evaporator 15.

  FIG. 14 is a cross-sectional view of the evaporator upper tank portion in the air flow direction in the present embodiment, and corresponds to FIG. 13 in the second embodiment. 15 is a cross-sectional view taken along the line CC in FIG.

  The capillary tube 17 in this embodiment is inserted into the upper tank 15b so as to penetrate the upper tank 15b of the first evaporator 15 in the tank longitudinal direction (left-right direction in FIG. 15).

  As a result, the outer surface of the capillary tube 17 is in direct contact with the refrigerant flowing in the left space 39 of the upper tank 15b of the first evaporator 15. Therefore, the outer surface of the capillary tube 17 is in contact with the outer surfaces of the tanks 15b and 15c. In comparison, the thermal resistance between the refrigerant flowing in the capillary tube 17 and the refrigerant flowing in the left space 39 of the upper tank 15b of the first evaporator 15 can be reduced.

  For this reason, heat exchange between the refrigerant flowing in the capillary tube 17 and the refrigerant flowing in the left space 39 of the upper tank 15b of the first evaporator 15 can be promoted, so that the cooling performance of the second evaporator 18 can be further improved.

  Further, when the outer surface of the capillary tube 17 is in direct contact with the refrigerant flowing in the left space 39 of the upper tank 15b, the pressure of the refrigerant flowing in the upper tank 15b acts on the outer surface side of the capillary tube 17. Therefore, the pressure difference between the inside and outside of the capillary tube 17 becomes the pressure difference between the refrigerant flowing in the capillary tube 17 and the refrigerant flowing in the upper tank 15b.

  Therefore, when the capillary tube 17 is disposed outside the upper tank 15b, that is, the pressure difference between the refrigerant flowing inside the capillary tube 17 and the air outside the capillary tube 17 (atmospheric pressure). Compared with the case where it is, the pressure difference inside and outside the capillary tube 17 can be reduced.

  For this reason, since the pressure resistance of the capillary tube 17 can be reduced as compared with the case where the capillary tube 17 is disposed outside the upper tank 15b, in this embodiment, the capillary tube is compared with the second embodiment. The plate thickness of 17 is reduced.

  Thus, by reducing the plate thickness of the capillary tube 17, the thermal resistance between the refrigerant flowing in the capillary tube 17 and the refrigerant flowing in the left side space 39 of the upper tank 15b can be further reduced.

  As a result, heat exchange between the refrigerant flowing in the capillary tube 17 and the refrigerant flowing in the left space 39 of the upper tank 15b can be further promoted, so that the cooling performance of the second evaporator 18 can be further improved.

(Fourth embodiment)
In the said 3rd Embodiment, although the capillary tube 17 is inserted in the upper tank 15b so that the upper tank 15b of the 1st evaporator 15 may be penetrated in a tank longitudinal direction, in this 4th Embodiment, it shows in FIG. Thus, the capillary tube 17 is inserted only in the left space 39 of the upper tank 15 b of the first evaporator 15.

  FIG. 16 is a cross-sectional view of the evaporator upper tank portion in the present embodiment, and corresponds to FIG. 15 in the third embodiment.

  In the present embodiment, a portion of the capillary tube 17 from the outlet side end portion (left end portion in FIG. 16) to the longitudinal intermediate portion is inserted into the left space 39 of the upper tank 15b, and the longitudinal intermediate portion of the capillary tube 17 is It protrudes outside the upper tank 15b.

  More specifically, a through hole 71 is formed in the lateral side surface portion (upper end portion in FIG. 16) of the left space 39 portion of the upper tank 15b, and the longitudinal intermediate portion of the capillary tube 17 is aired from the through hole 71. It protrudes outside the upper tank 15b toward the upstream side of the flow (the upper side in FIG. 16).

  And the site | part from the intermediate part of the capillary tube 17 to an exit side edge part (right edge part of FIG. 16) is extended along the outer surface of the upper tank 15b outside the upper tank 15b. In this example, the part from the middle part of the capillary tube 17 to the outlet side end part is in contact with the outer surface of the upper tank 15b.

  Thus, in this embodiment, since the capillary tube 17 is inserted only into the left space 39 of the upper tank 15b of the first evaporator 15, the intermediate pressure refrigerant flowing in the capillary tube 17 is transferred to the right side of the upper tank 15b. Heat exchange with a refrigerant having a low dryness flowing through the space 48 can be suppressed. As a result, the cooling performance of the second evaporator 18 can be further improved compared to the third embodiment.

  In the present embodiment, a through hole 71 is formed in the lateral side surface portion (upper end portion in FIG. 16) of the left space 39 of the upper tank 15b, and the longitudinal intermediate portion of the capillary tube 17 extends from the through hole 71. Although it protrudes outside the upper tank 15b toward the upstream side of the air flow (the upper side in FIG. 16), the through hole 71 of the upper tank 15b is located on the upper surface of the upper tank 15b (the front side in FIG. 16). The intermediate portion in the longitudinal direction of the capillary tube 17 may protrude outward from the upper tank 15b toward the upper side (front side in FIG. 16) from the through hole 71.

  Further, in this embodiment, the part from the middle part of the capillary tube 17 to the end on the outlet side is in contact with the outer surface of the upper tank 15b, but this part is connected to the outer surface of the upper tank 15b via a gap of a predetermined dimension. It may be separated.

  In this case, compared with the case where the part is brought into contact with the outer surface of the upper tank 15b, the intermediate pressure refrigerant flowing in the capillary tube 17 exchanges heat with a refrigerant having a low dryness flowing in the right space 48 of the upper tank 15b. Since this can be further suppressed, the cooling performance of the second evaporator 18 can be further improved.

(Fifth embodiment)
In each of the above embodiments, the first evaporator 15 is connected between the outlet side of the diffuser portion 14 d of the ejector 14 and the suction side filter of the compressor 11, and the blown air is cooled by the first and second evaporators 15 and 18. However, in the fifth embodiment, as shown in FIG. 17, the first first evaporator 15 is eliminated and the blown air is cooled only by the second evaporator 18. .

  FIG. 17 is a refrigerant circuit diagram of the vehicle ejector refrigeration cycle according to the present embodiment. In this embodiment, only the 2nd evaporator 18 and the capillary tube 17 are integrated, and the ejector 14 is comprised as a different body. That is, in the present embodiment, the integrated unit 20 as in each of the above embodiments is not configured.

  The outer surface of the capillary tube 17 is in contact with the outer surface of the left side space (a space portion located at the outlet of the refrigerant flow) 32 in the upper tank 18 b of the second evaporator 18. Thereby, heat exchange between the intermediate pressure refrigerant flowing in the capillary tube 17 and the refrigerant flowing in the left space 32 of the upper tank 18b of the second evaporator 18 is performed.

  For this reason, since the refrigerant passing through the refrigerant branch passage 16 is cooled by the refrigerant flowing in the left space 32 of the upper tank 18b, the refrigerant enthalpy difference (cooling capacity) between the refrigerant inlet and outlet in the second evaporator 18 is increased. The cooling performance of the second evaporator 18 can be improved.

  That is, the capillary tube 17 and the upper tank 18b in this embodiment are an internal heat exchanger that performs heat exchange between the high-temperature high-pressure refrigerant passing through the refrigerant branch passage 16 and the low-temperature low-pressure refrigerant downstream of the second evaporator 18. Playing a role.

  For this reason, compared with the case where an internal heat exchanger is provided separately, the cooling performance of the 2nd evaporator 18 can be improved, without causing deterioration of the mounting property to a vehicle and cost.

(Other embodiments)
In the first to fourth embodiments, the ejector 14, the first and second evaporators 15 and 18, and the capillary tube 17 are assembled as one integrated unit 20. There is no need to assemble, and only the first evaporator 15 and the capillary tube 17 may be integrated, and the ejector 14 and the second evaporator 18 may be configured separately.

  Moreover, in the said 1st-4th embodiment, although the capillary tube 17 is integrally brazed and fixed to the upper tank 15b etc. of the 1st evaporator 15, it does not necessarily need to be integrally brazed, such as a screw. The capillary tube 17 may be fixed to the upper tank 15b of the first evaporator 15 by mechanical coupling means.

  In the case of fixing by brazing, the part requiring sealing is sealed and joined by brazing. However, when fixing by mechanical coupling means, a sealing material is interposed in the part requiring sealing. It is necessary to ensure sealing performance.

  Moreover, although each said embodiment demonstrated the refrigeration cycle for vehicles, it cannot be overemphasized that this invention is applicable similarly not only for vehicles but to refrigeration cycles for stationary use.

It is a refrigerant circuit diagram of the ejector type refrigeration cycle for vehicles by a 1st embodiment of the present invention. It is a disassembled perspective view which shows schematic structure of the integrated unit by 1st Embodiment. It is a schematic perspective view which shows the refrigerant path structure of the integrated unit by 1st Embodiment. It is a longitudinal cross-sectional view by the side of the connection block of the evaporator tank part by 1st Embodiment. It is a longitudinal cross-sectional view on the opposite side to a connection block among the evaporator tank parts by 1st Embodiment. It is BB sectional drawing in FIG. It is a schematic perspective view of the connection block and interposition plate of the integrated unit by 1st Embodiment. It is C arrow line view of the connection block of FIG. It is a perspective view of the ejector fixing plate of the integrated unit by 1st Embodiment. It is a perspective view of the spacer of the integrated unit by 1st Embodiment. It is a perspective view of the partition plate of the integrated unit by 1st Embodiment. It is a perspective view of the refrigerant | coolant storage board of the integrated unit by 1st Embodiment. It is sectional drawing of the air flow direction of the evaporator upper side tank part by 2nd Embodiment. It is sectional drawing of the air flow direction of the evaporator upper side tank part by 3rd Embodiment. It is CC sectional drawing in FIG. It is sectional drawing of the evaporator upper side tank part by 4th Embodiment. It is a refrigerant circuit figure of the ejector type refrigeration cycle for vehicles by a 5th embodiment of the present invention.

Explanation of symbols

14 ... Ejector, 15 ... First evaporator, 15b ... Upper tank (tank),
16 ... Branch passage, 17 ... Capillary tube (throttle mechanism), 18 ... Second evaporator,
21 ... Tube, 39 ... Left tank space (space part).

Claims (5)

A compressor (11) for sucking and compressing refrigerant;
A radiator (13) that radiates heat of the high-pressure refrigerant discharged from the compressor (11);
Nozzle part (14a) for decompressing and expanding the refrigerant on the outlet side of the radiator (13), refrigerant suction port (14b) through which the refrigerant is sucked in by a jet refrigerant flow jetted from the nozzle part (14a), and the jet An ejector (14) having a booster (14d) for converting the velocity energy of the refrigerant flow obtained by mixing the refrigerant flow and the refrigerant sucked from the refrigerant suction port (14b) into pressure energy;
A first evaporator (15) that evaporates the refrigerant flowing out of the ejector (14) and exerts a cooling capacity;
A branch passage (16) for branching the refrigerant on the outlet side of the radiator (13) on the inlet side of the ejector (14) and leading it to the refrigerant suction port (14b);
A capillary tube (17) disposed in the branch passage (16) and serving as a throttling mechanism for decompressing the refrigerant on the outlet side of the radiator (13);
A second evaporator (18) disposed on the outlet side of the capillary tube (17) in the branch passage (16) and evaporating the refrigerant to exert a cooling capacity;
The first evaporator (15) includes a plurality of tubes (21) through which the refrigerant flows, and a tank (15b) that distributes or collects the refrigerant flow to the plurality of tubes (21).
The capillary tube (17) is adapted to exchange heat between the refrigerant flowing through the capillary tube (17) and the refrigerant flowing through the space (39) located at the outlet of the refrigerant flow in the tank (15b). An ejector refrigeration cycle, which is disposed in the tank (15b). The capillary tube (17) is disposed outside the tank (15b);
The ejector refrigeration cycle according to claim 1, wherein an outer surface of the capillary tube (17) is in contact with an outer surface of the space (39) in the tank (15b). The capillary tube (17) is disposed inside the space (39) of the tank (15b);
The ejector refrigeration cycle according to claim 1, wherein an outer surface of the capillary tube (17) is in direct contact with a refrigerant flowing through the space (39). The ejector refrigeration cycle according to any one of claims 1 to 3, wherein the capillary tube (17) is brazed integrally with the tank (15b). A compressor (11) for sucking and compressing refrigerant;
A radiator (13) that radiates heat of the high-pressure refrigerant discharged from the compressor (11);
Nozzle part (14a) for decompressing and expanding the refrigerant on the outlet side of the radiator (13), refrigerant suction port (14b) through which the refrigerant is sucked in by a jet refrigerant flow jetted from the nozzle part (14a), and the jet An ejector (14) having a booster (14d) for converting the velocity energy of the refrigerant flow obtained by mixing the refrigerant flow and the refrigerant sucked from the refrigerant suction port (14b) into pressure energy;
A branch passage (16) for branching the refrigerant on the outlet side of the radiator (13) on the inlet side of the ejector (14) and leading it to the refrigerant suction port (14b);
A capillary tube (17) disposed in the branch passage (16) and serving as a throttling mechanism for decompressing the refrigerant on the outlet side of the radiator (13);
An evaporator (18) disposed on the outlet side of the capillary tube (17) in the branch passage (16) to evaporate the refrigerant and exhibit a cooling capacity;
The evaporator (18) includes a plurality of tubes (21) through which the refrigerant flows, and a tank (18b) that distributes or collects the refrigerant flows to the plurality of tubes (21).
The capillary tube (17) is adapted to exchange heat between the refrigerant flowing through the capillary tube (17) and the refrigerant flowing through the space (32) located at the outlet of the refrigerant flow in the tank (18b). An ejector refrigeration cycle, which is disposed in the tank (18b).

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