JP2007192502A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger for uniformly distributing heat exchanging fluid into a plurality of fluid passages even when there is a small flowing amount of heat exchanging fluid. <P>SOLUTION: The heat exchanger comprises the plurality of fluid passages 21 in which the heat exchanging fluid including at least liquid-phase fluid flows, and a tank 18b arranged above inlet portions 21a of the plurality of fluid passages 21 for distributing the flow of the heat exchanging fluid into the plurality of fluid passages 21. In the tank 18b above the inlet portions 21a, fluid reservoirs 75, 77, 80 are arranged for reserving once the liquid-phase fluid flowing into the tank 18b. The liquid-phase fluid overflowing from the reservoirs 75, 77, 80 drops onto the inlet portions 21a. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a heat exchanger having a plurality of fluid passages, and is suitable for use in, for example, an evaporator of an ejector refrigeration cycle.

  2. Description of the Related Art Conventionally, an ejector refrigeration cycle having an ejector serving as a refrigerant decompression unit and a refrigerant circulation unit is known. This ejector-type refrigeration cycle is effective when applied to, for example, a vehicle air conditioner, or a vehicle refrigeration device that freezes and refrigerates on-board luggage. Further, it is effective when applied to a stationary refrigeration cycle system such as an air conditioner, a refrigerator, a freezer and the like. This type of ejector refrigeration cycle is known from Patent Document 1 and the like.

  In addition, the applicant of the present application previously described a specific application in the ejector-type refrigeration cycle of Patent Document 1 in a patent application (hereinafter referred to as a prior application example) of Japanese Patent Application No. 2005-37645 (Japanese Patent Application Laid-Open No. 2005-308384). Proposed configuration.

  In this prior application example, the first evaporator is disposed on the outlet side of the ejector that functions as the refrigerant decompression means and the refrigerant circulation means, and the outlet side of the first evaporator is connected to the suction side of the compressor. An ejector refrigeration cycle is disclosed in which a refrigerant branch passage branching from an upstream portion 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. ing.

  According to the ejector-type refrigeration cycle of the prior application, the pressure drop caused 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 speed of the refrigerant at the time of expansion Since the 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.

  Further, the first and second evaporators can exert heat absorption (cooling) action on separate spaces, or the first and second evaporators on the same space.

Further, in this prior application example, a tank part into which the refrigerant that has passed through the refrigerant branch passage flows is arranged above the second evaporator, and this tank part is connected to a plurality of refrigerant passages (tubes) of the second evaporator. The refrigerant is distributed. For this reason, distribution of the refrigerant | coolant with respect to the several tube of a 2nd evaporator is realizable by simple structure.
Japanese Patent No. 3322263

  By the way, in the ejector refrigeration cycle of the prior application example, the refrigerant branched in the refrigerant branch passage flows into the tank portion of the second evaporator. In other words, since only a part of the refrigerant circulating in the refrigeration cycle flows into the tank portion of the second evaporator, the flow rate of the refrigerant flowing into the tank portion is small.

  For this reason, the refrigerant reaches the space close to the inlet of the refrigerant in the space in the tank portion, but the refrigerant does not easily reach the space away from the inlet of the refrigerant, so the distribution of the refrigerant to the tubes is uniform. It becomes inadequate.

  As a result, it is difficult to make the heat absorption (cooling) action by the plurality of tubes uniform, and there is a problem that the uniformity of the temperature distribution of the air that has passed through the second evaporator becomes insufficient.

  In the heat exchanger in which the heat exchange fluid (for example, hot water) is distributed to the plurality of internal passages by the tank unit, the same problem occurs when the flow rate of the heat exchange fluid is small.

  An object of this invention is to provide the heat exchanger which can equalize | distribute the heat exchange fluid with respect to a some fluid channel | path even if the flow volume of a heat exchange fluid is small in view of the said point.

To achieve the above object, the present invention provides a plurality of fluid passages (21) through which a heat exchange fluid including at least a liquid phase fluid flows,
A tank (18b) that is disposed above the inlet portions (21a) of the plurality of fluid passages (21) and distributes the heat exchange fluid flow to the plurality of fluid passages (21),
Storage members (75, 77, 80) for temporarily storing the liquid phase fluid that has flowed into the tank (18b) are disposed inside the tank (18b) and above the inlet (21a).
The liquid phase fluid overflowing from the storage member (75, 77, 80) is configured to fall to the inlet portion (21a) side.

  According to this, the liquid phase fluid of the heat exchange fluid is temporarily stored by the storage member (75, 77, 80), and the liquid phase fluid overflowing from the storage member (75, 77, 80) flows into the fluid passage (21). Therefore, the fluid passage in the position where the liquid-phase fluid is prevented from flowing directly into the fluid passage (21) in the position where the liquid-phase fluid is easily reachable among the plurality of fluid passages (21), and the liquid-phase fluid is difficult to reach directly. The liquid phase fluid can be guided to (21).

  For this reason, even if the flow rate of the heat exchange fluid is small, the distribution of the heat exchange fluid to the plurality of fluid passages (21) can be made uniform.

Specifically, in the present invention, the storage member (75) is formed in a cross-sectional mountain shape,
A valley-shaped storage part (76) is formed by the bottom part (75d) having a mountain-shaped cross section and the inner wall surface (60b) extending in the vertical direction of the tank (18b),
Furthermore, the hole (75a) is formed in the top part of the cross-sectional mountain shape among the storage members (75),
The liquid phase fluid once accumulates in the reservoir (76), and the liquid phase fluid accumulated in the reservoir (76) falls through the hole (75a).

  As a result, the liquid phase fluid can be temporarily stored in the storage member (75, 77, 80), and the liquid phase fluid overflowing from the storage member (75, 77, 80) is dropped to the inlet (21a) side. be able to.

  More specifically, in the present invention, when the bending angle (θ) of the cross-sectional mountain shape is set in the range of 30 degrees or more and 170 degrees or less, the liquid phase fluid is stored and dropped by the storage member (75, 77, 80). It was found that the heat exchange fluid can be more evenly distributed to the plurality of fluid passages (21).

  In the present invention, specifically, the hole (75a) is arranged so as to overlap with the inlet (21a).

  Thereby, since the liquid phase fluid which fell through the hole part (75a) can be directly flowed in in the fluid channel | path (21), distribution of a heat exchange fluid can be made more uniform.

  In the present invention, specifically, the edge of the hole (75a) is formed in a wave shape.

  According to this, the liquid phase fluid is in a droplet state due to the surface tension generated at the edge of the hole (75a), but the liquid phase fluid is a large liquid by making the edge of the hole (75a) corrugated. It can be prevented from becoming drops. In other words, the liquid phase fluid can be dropped from the hole (75a) in a small droplet state. For this reason, the distribution of the heat exchange fluid can be made more uniform.

  The “wave shape” in the present invention does not mean only a smooth wave shape formed by a curve, but also includes a sharp wave shape formed by a straight line.

In the present invention, more specifically, the edge of the hole (75a) is formed in a wave shape,
The hole (75a) is arranged so that the top (75c) of the corrugated shape that is recessed outside the hole (75a) overlaps with the inlet (21a).

  Thus, the liquid phase fluid that has dropped from the top portion (75c) that is recessed outside the hole portion (75a) in the wave shape can be directly flowed into the fluid passage (21). (21) can be effectively introduced.

Further, according to the present invention, the refrigerant is sucked from the refrigerant suction port (14b) by the high-speed refrigerant flow ejected from the nozzle portion (14a), and the refrigerant jetted from the nozzle portion (14a) and the refrigerant suction port (14b). An ejector (14) for mixing and discharging the refrigerant sucked from
A first evaporator (15) for evaporating the refrigerant discharged from the ejector (14);
A second evaporator (18) for evaporating the refrigerant sucked into the refrigerant suction port (14b),
The 2nd evaporator (18) is comprised by the heat exchanger by the above-mentioned this invention.

  According to this, since the second evaporator (18) is arranged in the branched refrigerant flow, the flow rate of the refrigerant flowing into the second evaporator (18) decreases, but the second evaporator (18) Since it comprises the heat exchanger according to the present invention described above, the effects of the present invention described above can be exhibited with respect to the second evaporator (18).

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

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. The present embodiment is an example in which the heat exchanger according to the present invention is applied to an ejector refrigeration cycle. The ejector-type refrigeration cycle unit can also be called an ejector-type refrigeration cycle evaporator unit or an ejector-equipped evaporator unit.

  The ejector-type refrigeration cycle unit is connected to a condenser, which is another component of the refrigeration cycle, and a compressor via a pipe in order to configure a refrigeration cycle including the ejector. In one form, the ejector-type refrigeration cycle unit is used as an indoor unit for cooling air. In addition, the ejector refrigeration cycle unit can be used as an outdoor unit in another form.

  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 portion 14 e (the tip portion 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 throttling mechanism 17 is a pressure reducing means that adjusts the refrigerant flow rate to the second evaporator 18, and can be specifically constituted by a fixed throttle such as a capillary tube or an orifice.

  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 with reference to FIGS.

  FIG. 2 is an exploded perspective view showing an outline of the overall configuration of the first and second evaporators 15 and 18. FIG. 3 is a cross-sectional view of the upper tank portion of the first and second evaporators 15 and 18, FIG. 4 is a vertical cross-sectional view of the upper tank portion of the second evaporator 18, and FIG. It is an expanded sectional view.

  First, a specific example of an integrated structure of the two evaporators 15 and 18 will be described with reference to FIG. In the example of FIG. 2, 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. The tube 21 corresponds to a heat source fluid passage in the present invention. 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.

  In FIG. 2, only a part of the fins 22 is illustrated, but the fins 22 are disposed over the entire heat exchange core portions 15 a and 18 a, and the tubes 21 and the fins 22 are disposed over the entire heat exchange core portions 15 a and 18 a. A laminated structure is configured. And the ventilation air of the electric blower 19 passes through the space | gap part of this 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.

  As shown in FIG. 5, the upper and lower tank portions 15b and 15c of the first evaporator 15 have tube fitting hole portions 15d into which the upper and lower ends of the tube 21 of the heat exchange core portion 15a are inserted and joined. The upper and lower ends of the tube 21 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 hole portions 18d into which the upper and lower ends of the tube 21 of the heat exchange core portion 18a are inserted and joined. Both upper and lower end portions communicate with the internal space 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.

  In FIG. 5, only the tube fitting hole on the upper tank 15b, 18b side is shown in the tube fitting holes 15d, 18d of the tank parts 15b, 15c, 18b, 18c on both the upper and lower sides. On the other hand, since the tube fitting hole on the lower tanks 15c and 18c has the same configuration as the tube fitting hole on the upper tanks 15b and 18b, the tube fitting holes on the lower tanks 15c and 18c are provided. Is not shown.

  Since the two upper tanks 15b and 18b and the two lower tanks 15c and 18c are adjacent to each other, the two upper tanks 15b and 18b and the two lower tanks 15c and 18c can be integrally formed. . Of course, the two upper tanks 15b and 18b and the two lower tanks 15c and 18c may be formed as independent members.

  In the present embodiment, as shown in FIGS. 2 and 5, the two upper tanks 15 b and 18 b are divided and formed into a bottom surface side half crack member 60, a top surface side half crack member 61 and a cap 62.

  More specifically, the bottom half crack member 60 has a substantially W-shaped cross section in which the bottom half crack portions of the two upper tanks 15b and 18b are integrally formed. Each of the upper tanks 15b, 18b has a substantially M-shaped cross section formed by integrally molding the upper surface side half cracks.

  A plane portion 60 a is formed at the center of the substantially W-shaped cross section of the bottom surface side half-cracked member 60, and a plane portion 61 a is formed at the center of the approximately M-shaped cross section of the top surface side half-cracked member 61. Then, when the bottom surface side half-cracked member 60 and the top surface side half-cracked member 61 are combined in the vertical direction, the flat surface portion 60a and the flat surface portion 61a are in close contact to form two cylindrical shapes. Further, two upper tanks 15b and 18b are configured by closing one end portion in the longitudinal direction of the two cylindrical shapes (the right end portion in FIG. 2) with a cap 62.

  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 the present embodiment, the connection block 23 and the capillary tube 17a constituting the throttle mechanism 17 shown in FIG. 2 are also assembled integrally with the first and second evaporators 15 and 18 by brazing.

  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 intended.

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

  More specifically, the assembly structure of the ejector 14, the capillary tube 17a, the connection block 23, and the like will be described. The capillary tube 17a and the connection block 23 are formed of an aluminum material in the same manner as the evaporator parts.

  As shown in FIG. 5, the capillary tube 17 a is disposed so as to be sandwiched between valley portions 61 b formed above the flat surface portion 61 a of the upper surface side half-cracked member 61 of the upper tanks 15 b and 18 b.

  The connection block 23 is a member that is brazed and fixed to a side surface of one of the first and second evaporators 15 and 18 in the longitudinal direction of the upper tanks 15b and 18b (left side in FIG. 2). One refrigerant inlet 25 of the integrated unit 20 shown, one refrigerant outlet 26, and the ejector inlet part 63 for assembling the ejector 14 to the evaporator side are comprised.

  As shown in FIGS. 3 and 6, in the middle of the connection block 23 in the thickness direction, the refrigerant inlet 25 is connected to the main passage 25a that forms the first passage toward the inlet side of the ejector 14 and the inlet side of the capillary tube 17a. It branches into the branch passage 16 which makes the 2nd passage which goes. This branch passage 16 corresponds to the inlet portion of the branch passage 16 in FIG. Accordingly, the branch point Z in FIG. 1 is configured inside the connection block 23.

  On the other hand, the refrigerant outlet 26 is configured by one simple passage hole (circular hole or the like) penetrating in the thickness direction of the connection block 23.

  The connection block 23 is brazed and fixed to the side surfaces of the upper tanks 15b and 18b via an intervening plate 64. The intervening plate 64 plays a role of forming the main passage 25a and the branch passage 16 and fixing the ejector 14 in the longitudinal direction by being fixed integrally with the connection block 23.

  The intervening plate 64 formed of an aluminum material is connected to a main passage side opening 64a communicating with the main passage 25a of the connection block 23, a branch passage side opening 64b communicating with the branch passage 16 of the connection block 23, and A refrigerant outlet side opening 64c communicating with the refrigerant outlet 26 of the block 23 is formed.

  A cylindrical portion 64d inserted into the upper tank 18b is formed at the peripheral edge of the main passage side opening 64a, and an annular flange protruding in the inner diameter direction of the cylindrical portion 64d is formed at the tip of the cylindrical portion 64d. A portion 64e is formed.

  By caulking the first claw portion 64f protruding from the interposition plate 64 toward the evaporator to the upper tanks 15b and 18b, the interposition plate 64 can be temporarily fixed to the evaporator side. Furthermore, the connection block 23 can be temporarily fixed to the evaporator side by caulking the second claw portion 64g protruding from the interposition plate 64 to the connection block 23 side.

  The branch passage side opening 64b of the intervening plate 64 is sealed and joined to the upstream end (left end in FIG. 2) of the capillary tube 17a by brazing.

  By configuring the connection block 23 and the interposition plate 64 in this way, the refrigerant outlet 26 of the connection block 23 communicates with the left space 31 of the upper tank 15b via the refrigerant outlet side opening 64c of the interposition plate 64, and is connected. The main passage 25a of the block 23 communicates with the left space 27 of the upper tank 18b via the main passage side opening 64a of the interposition plate 64, and the branch passage 16 of the connection block 23 communicates with the branch passage side opening of the interposition plate 64. The connection block 23 and the intervening plate 64 are brazed to the side surfaces of the upper tanks 15b and 18b in a state where they communicate with the upstream end 17c of the capillary tube 17a via 64b.

  The ejector fixing plate 65 is a member that fixes the diffuser portion 14 d of the ejector 14 and plays a role of partitioning the internal space of the upper tank 18 b into the left space 27 and the right space 28. The left space 27 of the upper tank 18b serves as a collecting tank that collects the refrigerant that has passed through the plurality of tubes 21 of the second evaporator 18.

  The ejector fixing plate 65 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.

  As shown in FIG. 7, the ejector fixing plate 65 includes a flat plate portion 65a facing the longitudinal direction of the upper tank 18b (left and right direction in FIG. 7), and a cylindrical portion 65b protruding from the flat plate portion 65a in the longitudinal direction of the upper tank 18b. And a claw portion 65c protruding upward from the upper end of the flat plate portion 65a, and is formed of an aluminum material.

  The internal space of the cylindrical portion 65b forms a through hole that penetrates the ejector fixing plate 65 in the left-right direction. As shown in FIG. 4, the claw portion 65c passes through the slit-like hole 66 on the upper surface of the upper tank 18b and is caulked to the upper tank 18b. Thereby, the ejector fixing plate 65 can be temporarily fixed to the upper tank 18b.

  As shown in FIG. 4, the downstream end portion (right end side) 17d of the capillary tube 17a is inserted into the upper tank 18b in the stacking direction of the tubes 21 (left-right direction in FIG. 4). More specifically, the downstream end 17d of the capillary tube 17a is inserted into the through hole 62a of the cap 62 of the upper tank 18b and opens into the right space 28. The outer peripheral surface of the capillary tube 17a and the through hole 62a of the cap 62 are sealed and joined by brazing.

  An upper and lower partition plate 67 is disposed at a substantially central portion in the vertical direction of the right space 28 in the upper tank 18b. The upper and lower partition plates 67 are members that play a role of partitioning the right space 28 into two spaces in the vertical direction, that is, the upper space 69 and the lower space 70. The lower space 70 serves as a distribution tank that distributes the refrigerant to the plurality of tubes 21 of the second evaporator 18.

  The upper and lower partition plates 67 are members made of aluminum material and brazed to the inner wall surface of the upper tank 18b, and have a plate shape that extends in the longitudinal direction of the upper tank 18b as a whole as shown in FIG. .

  More specifically, the upper and lower partition plates 67 include a flat plate surface 67a extending in the longitudinal direction of the upper tank 18b, and first and second bent portions that are bent at right angles in opposite directions at both longitudinal ends of the flat plate surface 67a. 67b and 67c.

  The first bent portion 67b is bent upward from the end of the flat plate surface 67a near the downstream end 17d of the capillary tube 17a (the right side in FIG. 4), and the second bent portion 67c is a flat plate. It is bent downward from the other end of the surface 67a.

  As shown in FIG. 5, the flat plate surface 67a is inclined so as to become lower from the first evaporator 15 side toward the second evaporator 18 side. A rib 67d protruding in a triangular shape toward the flat plate surface 67a is integrally formed at the base of the first bent portion 67b. The rib 67d increases the rigidity of the first bent portion 67b, thereby maintaining the bending angle of the first bent portion 67b at a right angle.

  As shown in FIG. 4, the claw portion 67e protruding upward from the tip end portion (upper end portion) of the first bent portion 67b passes through the slit-shaped hole 68 on the upper surface of the upper tank 18b and is caulked to the upper tank 18b. Thereby, the upper and lower partition plates 67 can be temporarily fixed to the upper tank 18b.

  By forming the first bent portion 67b in the upper and lower partition plates 67, the lower space 70 is expanded upward on the downstream end portion 17d side (right side in FIG. 4) of the capillary tube 17a with respect to the first bent portion 67b. Has been. In other words, the upper space 69 is not formed in the space on the downstream end 17 d side of the capillary tube 17 a in the right space 28, and the lower space 70 is formed over the entire vertical space of the right space 28.

  As shown in FIG. 8, a recessed portion 67 f that is recessed toward the lower space 70 is formed at the end of the flat surface 67 a of the upper and lower partition plates 67 on the second bent portion 67 c side (left side in FIG. 8). Has been. The recess 67f is composed of a cylindrical recess 67g and a conical recess 67h.

  The cylindrical recess 67g has a shape extending in the longitudinal direction of the flat plate surface 67a at the end of the flat plate surface 67a on the second bent portion 67c side (left side in FIG. 8). The conical concave portion 67h is formed continuously with the cylindrical concave portion 67g on the first bent portion 67b side (the right side in FIG. 8) from the cylindrical concave portion 67g, and the cylindrical concave portion 67g side becomes deeper away from the cylindrical concave portion 67g. It has a shallow shape.

  The ejector 14 is made of a metal material such as copper or aluminum, but may be made of a resin (non-metal material). After the assembly process (brazing process) for integrally brazing the first and second evaporators 15, 18, etc., the ejector 14 is formed in the hole shape of the ejector inlet 63 of the connection block 23 and the main passage side of the interposed plate 64. It penetrates the hole shape of the opening 64a and is inserted into the upper tank 18b.

  Here, the front end portion 14e in the longitudinal direction of the ejector 14 shown in FIG. 3 is a portion corresponding to the outlet portion 14e of the ejector 14 in FIG. This ejector tip portion 14e is inserted into the cylindrical portion 65b of the ejector fixing plate 65, and is fixed with a seal using an O-ring 29a.

  As shown in FIG. 4, the ejector tip portion 14 e is disposed at a position straddling the flat plate surface 67 a of the upper and lower partition plates 67 in the vertical direction, but a recess 67 f is formed in the upper and lower partition plates 67 and the ejector 14. Since the outer peripheral surface of the diffuser portion 14d is disposed on the cylindrical recess 67g of the recess portion 67f, the entire ejector tip portion 14e opens into the upper space 69 of the right space 28 in the upper tank 18b. Further, the refrigerant suction port 14 b of the ejector 14 communicates with the left space 27 of the upper tank 18 b of the second evaporator 18.

  As shown in FIG. 3, a left and right partition plate 30 is disposed at a substantially central portion in the longitudinal direction of the inner space of the upper tank 15 b of the first evaporator 15, and the inner space of the upper tank 15 b is elongated by the left and right partition plates 30. It is divided into two spaces in the direction, that is, a left space 31 and a right space 32.

  Here, the left space 31 serves as a collection tank that collects the refrigerant that has passed through the plurality of tubes 21 of the first evaporator 15, and the right space 32 corresponds to the plurality of tubes 21 of the first evaporator 15. It serves as a distribution tank that distributes refrigerant.

  By the way, as shown in FIG. 4, the recessed part 61c is in the site | part located in the upper space 69 of the right side space 28 in the upper side tank 18b among the flat surface 61a of the upper surface side half crack member 61 of the upper side tanks 15b and 18b. Is formed.

  A plurality of the recesses 61c are arranged in the stacking direction of the tubes 21 (the left-right direction in FIG. 4). A plurality of communication holes 71 are formed by a space surrounded by the recess 61c and the flat plate surface 60a of the bottom side half crack member 60 of the upper tanks 15b and 18b.

  Through the plurality of communication holes 71, the upper space 69 of the right space 28 in the upper tank 18b and the right space 32 of the upper tank 15b of the first evaporator 15 communicate with each other.

  Note that the communication holes 71 may be formed over almost the entire region in the left-right direction of the upper space 69 (in the stacking direction of the tubes 21) by forming the plurality of recesses 61c into a single shape.

  The left end portion (left end portion in FIG. 3) in the longitudinal direction of the ejector 14 is a portion corresponding to the inlet portion of the nozzle portion 14a in FIG. 1, and this left end portion is formed on the cylindrical portion 64d of the interposition plate 64 using an O-ring 29b. Fitted to the inner peripheral surface and fixed with a seal.

  In the present embodiment, the ejector 14 is fixed in the longitudinal direction as follows. First, after the ejector 14 is inserted into the upper tank 18b from the ejector inlet 63 of the connection block 23, the spacer 72 is inserted into the ejector inlet 63, and the male screw on the outer peripheral surface of the cylindrical plug 73 is inserted into the ejector. Screwed into the female screw on the inner peripheral surface of the inlet portion 63. In this example, the spacer 72 and the plug 73 are each formed of an aluminum material.

  As shown in FIG. 9, the spacer 72 includes an annular portion 72a and a protruding portion 72b that protrudes in the axial direction from a part of the annular portion 72a. For this reason, when the plug 73 is screwed into the ejector inlet 63, the protrusion 72 b of the spacer 72 presses the left end of the ejector 14 in the insertion direction of the ejector 14.

  On the other hand, an annular portion 74 having a larger diameter is formed at the left end portion of the ejector 14. For this reason, when the protruding portion 72 b of the spacer 72 presses the left end portion of the ejector 14 in the insertion direction of the ejector 14, the annular portion 74 of the ejector 14 is pressed against the flange portion 64 e of the interposed plate 64. In this way, the ejector 14 can be fixed in the longitudinal direction.

  Here, if the protruding portion 72b is formed so as to protrude from the entire circumference of the annular portion 72a of the spacer 72 and the spacer 72 has a simple cylindrical shape, the main passage 25a of the connection block 23 is blocked by the spacer 72. .

  On the other hand, in this embodiment, since the protrusion 72b of the spacer 72 is formed so as to protrude from only a part of the annular portion 72a of the spacer 72, the main passage 25a of the connection block 23 is closed. Therefore, the ejector 14 can be fixed in the longitudinal direction.

  The outer peripheral surface of the cylindrical plug 73 is fitted and sealed with the inner peripheral surface of the ejector inlet portion 63 of the connection block 23 using an O-ring 29c.

  As shown in FIGS. 4 and 5, a refrigerant storage plate 75 is disposed in the lower space 70 of the right space 28 in the upper tank 18b. This refrigerant | coolant storage board 75 is a member which plays the role which equalizes distribution of the refrigerant | coolant with respect to the some tube 21 of the 2nd evaporator 18, and corresponds to the storage member in this invention.

  In this example, the refrigerant storage plate 75 is formed of an aluminum material, and has a plate shape extending in the stacking direction of the tubes 21 (the left-right direction in FIG. 4) in a cross-sectional mountain shape.

  As shown in FIG. 10, a plurality of holes 75 a are formed in the stacking direction of the tubes 21 at the top of the refrigerant storage plate 75 having a mountain-shaped cross section. A connecting portion 75b having a mountain-shaped cross section is formed between the holes 75a, and the rigidity of the refrigerant storage plate 75 can be ensured by the connecting portion 75b even if the hole 75a is formed.

  As shown in FIG. 10, the hole 75 a has a shape that extends in the stacking direction of the tubes 21 as a whole. Since the edge part extended in the lamination direction of the tube 21 among the hole parts 75a has a wave shape, the several peak part 75c hollowed in the outer side of the hole part 75a is formed in the said edge part. On the other hand, the edge part extended in the direction orthogonal to the lamination direction of the tube 21 among the hole parts 75a has a linear shape.

  In this example, the wave shape at the edge of the hole 75a is formed into a sharp shape by a straight line. In addition, you may form the wave shape in the edge part of the hole 75a in the smooth shape by a curve.

  As shown in FIG. 5, the end 75e of the refrigerant reservoir plate 75 on the side of the skirt 75d having a mountain-shaped cross section is placed on the upper end surface of the tube 21 and extends in the vertical direction of the bottom half-crack member 60 of the upper tank 18b. It is brazed to the wall surface 60b. As a result, a valley-shaped reservoir 76 is formed between the skirt 75d of the refrigerant reservoir 75 and the inner wall surface of the upper tank 18b.

  In this example, as shown in FIG. 11, the interval P between the wave-shaped top portions 75 c of the hole 75 a is set to be the same as the interval between the tubes 21, so that the top portion 75 c overlaps with the inlet portion 21 a of the tube 21. It is supposed to be.

  In the above configuration, the refrigerant flow path of the integrated unit 20 as a whole will be specifically described with reference to FIGS. FIG. 12 is a schematic perspective view showing the entire refrigerant flow path of the integrated unit 20.

  The refrigerant inlet 25 of the connection block 23 is branched into a main passage 25 a and a branch passage 16. The refrigerant in the main passage 25a passes through the main passage side opening 64a of the intervening plate 64 and is then reduced in pressure through the ejector 14 (nozzle part 14a → mixing part 14c → diffuser part 14d). It flows into the right space 32 of the upper tank 15b of the first evaporator 15 as shown by the arrow a through the upper space 69 of the right space 28 in the upper tank 18b and the plurality of communication holes 71.

  The refrigerant in the right space 32 descends the plurality of tubes 21 on the right side of the heat exchange core 15a as indicated by the arrow b and flows into the right side in the lower tank 15c. 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 rises up the plurality of tubes 21 on the left side of the heat exchange core part 15a as shown by the arrow d and flows into the left space 31 of the upper tank 15b. It flows to the refrigerant outlet 26 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 is first depressurized through the capillary tube 17a, and the low-pressure refrigerant (gas-liquid two-phase refrigerant) after this depressurization is supplied to the second evaporator 18 as indicated by an arrow f. It flows into the lower space 70 of the right space 28 of the upper tank 18b.

  The refrigerant that has flowed into the lower space 70 descends the plurality of tubes 21 on the right side of the heat exchange core portion 18a as indicated by the arrow g and flows into the right side of the lower tank 18c. Since the left and right partition plates are not 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 heat exchange core 18a as indicated by arrow i and flows into the left space 27 of the upper tank 18b. Since the refrigerant suction port 14b of the ejector 14 communicates with the left space 27, the refrigerant in the left space 27 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 25 may be provided in the connection block 23 as a whole, and one refrigerant outlet 26 is 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 25 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 25a 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 17a.

  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 through 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 26 and compressed again.

  On the other hand, the refrigerant flow flowing into the refrigerant branch passage 16 is depressurized by the capillary tube 17a to become a low-pressure refrigerant (gas-liquid two-phase refrigerant), and this low-pressure refrigerant is the refrigerant flow indicated by arrows f to i in FIG. The refrigerant flows through the road. 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.

  Further, under the condition where the cycle heat load is small, the high / low pressure difference of the cycle becomes small and the input of the ejector 14 becomes small. In this case, in the cycle of Patent Document 1, since the flow rate of the refrigerant passing through the second evaporator 18 depends only on the refrigerant suction capability of the ejector 14, the input reduction of the ejector 14 → the reduction of the refrigerant suction capability of the ejector 14 → the second The refrigerant flow rate of the second evaporator 18 decreases, and it is difficult to ensure the cooling performance of the second evaporator 18.

  On the other hand, according to the present embodiment, the 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 14b through the refrigerant branch passage 16. A parallel connection with the ejector 14 is established.

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

  By the way, in the ejector type refrigeration cycle 10 in the present embodiment, the refrigerant in the gas-liquid two-phase state (intermediate pressure refrigerant) after passing through the expansion valve 13 flows into the refrigerant flow from the main passage 25a of the connection block 23 toward the ejector 14, and the connection block. The refrigerant flow is divided into the refrigerant flow from the refrigerant branch passage 16 to the capillary tube 17a.

  For this reason, since the flow rate of the refrigerant (arrow f) flowing from the capillary tube 17a into the lower space 70 of the right space 28 of the upper tank 18b of the second evaporator 18 decreases, the lower space 70 (distribution tank) The refrigerant hardly reaches the side away from the downstream end 17d of the capillary tube 17a.

  As a result, in the lower space 70 (distribution tank), the distribution of the refrigerant to the plurality of tubes 21 becomes non-uniform, so the temperature distribution of the cold air cooled by the second evaporator 18 becomes non-uniform.

  Therefore, in the present embodiment, as indicated by an arrow j in FIG. 5, the liquid refrigerant of the gas-liquid two-phase refrigerant flowing into the lower space 70 from the capillary tube 17 a is formed at the skirt 75 d of the refrigerant storage plate 75. The liquid refrigerant that once accumulates in the valley-shaped reservoir 76 and overflows from the valley-shaped reservoir 76 falls from the plurality of holes 75a of the refrigerant reservoir 75 to the tube 21 side.

  Thereby, since the liquid refrigerant can be guided to the side away from the downstream end 17d of the capillary tube 17a in the lower space 70 (distribution tank), the plurality of tubes 21 inserted into the lower space 70 are provided. The distribution of the refrigerant can be made uniform. For this reason, the temperature distribution of the cold air cooled by the second evaporator 18 can be made uniform.

  According to a detailed study by the present inventor, if the bending angle θ (FIG. 5) of the cross-sectional mountain shape of the refrigerant storage plate 75 is set in a range of 30 degrees to 170 degrees, It was found that the falling can be performed appropriately, and the distribution of the refrigerant to the plurality of tubes 21 can be made more uniform.

  Further, according to a detailed examination by the present inventor, when the edge of the hole 75a of the refrigerant reservoir plate 75 is linear, the liquid refrigerant is relatively large liquid due to the surface tension generated at the edge of the hole 75a. It was found that the effect of uniform distribution of the refrigerant was impaired because the droplets dropped from the hole 75a to the tube 21 side.

  Therefore, in the present embodiment, as shown in FIG. 11, the edge portion extending in the stacking direction of the tube 21 in the hole portion 75 a of the refrigerant reservoir plate 75 is wave-shaped, so that the liquid refrigerant due to the surface tension is relatively large. The liquid droplet refrigerant can fall from the hole 75a before becoming a large liquid droplet.

  In other words, since the liquid refrigerant can be dropped from the hole 75a to the tube 21 side in a small droplet state, the effect of making the refrigerant distribution uniform can be effectively exhibited.

  In addition, the liquid refrigerant collected in the storage part 76 overflows and falls mainly from the top part 75c located in the lowest part among the edge parts of the hole part 75a. Therefore, in this embodiment, as shown in FIG. 11, the interval P between the corrugated top portions 75 c is set to be the same as the interval between the tubes 21, and the corrugated top portion 75 c overlaps with the inlet portion 21 a of the tube 21. Like to do.

  Thereby, since the liquid refrigerant that has overflowed and dropped from the top portion 75 c can be directly flowed into the tube 21, the liquid refrigerant can be effectively flowed into the tube 21.

  By the way, FIGS. 13-15 is the application example 1 and it can be set as embodiment of this invention by applying this invention with respect to this application example 1. FIG. FIG. 13 is a perspective view showing an outline of the overall configuration of the integrated unit 20 of the application example 1, and FIG. 14 is a cross-sectional view of the upper tank portions of the first and second evaporators 15 and 18 in the application example 1. FIG. 15 is a longitudinal sectional view of the upper tank portion of the second evaporator 18 in Application Example 1. FIG.

  In this application example 1, the capillary tube 17a is disposed inside the upper tank 18b. That is, the downstream end 17d of the capillary tube 17a passes through the support hole 24a of the second connection block 24 and opens into the right space 28 of the upper tank 18b as shown in FIG. In Application Example 1, the refrigerant storage plate 75 is not disposed in the right space 28.

  Further, the connection block 23 in the application example 1 corresponds to the connection block 23 and the intervening plate 64 in the present embodiment formed integrally. In Application Example 1, the ejector inlet portion 63 is not formed, and the ejector 14 is inserted into the upper tank 18 b of the second evaporator 18 from the refrigerant inlet 25. Therefore, the spacer 72 and the plug 73 in this embodiment are unnecessary.

  Further, in place of the ejector fixing plate 65 in the present embodiment, the second connection block 24 is arranged at the center in the longitudinal direction in the upper tank 18b, and the internal space of the upper tank 18b is divided into right and left by the second connection block 24. Yes.

  And since the upper and lower partition plates 67 in this embodiment are not arranged, the right space 28 inside the upper tank 18b of the second evaporator 18 is made into one space without partitioning into the upper space 69 and the lower space 70. Yes.

  Further, instead of the communication hole 71 in the present embodiment, the communication hole portion 24c of the second connection block 24 is connected to the upper tank of the first evaporator 15 via the through hole 33a of the intermediate wall surface 33 of both the upper tanks 15b and 18b. It communicates with the right space 32 of 15b.

  Therefore, the low-pressure refrigerant discharged from the diffuser portion 14d of the ejector 14 passes through the communication hole portion 24c of the second connection block 24 and the through hole 33a of the intermediate wall surface 33, and then the upper tank of the first evaporator 15 as indicated by the arrow a. It flows into the right space 32 of 15b.

  By applying the present invention to this application example 1, an embodiment of the present invention can be obtained. Specifically, if the refrigerant storage plate 75 is arranged in the right space 28, the refrigerant flowing into the right space 28 from the downstream end 17 d of the capillary tube 17 a can be uniformly distributed to the plurality of tubes 21.

  16 to 18 are an application example 2. In this application example 2, the capillary tube 17a is disposed between the branch passage 16 of the first connection block 23 of the integrated unit 20 and the inlet side of the second evaporator 18, and the second evaporation is performed in the capillary tube 17a. In the application example 2 of FIGS. 16 to 18, the capillary tube 17 a is not adopted as the pressure reducing means of the second evaporator 18, and instead the first connection block is used. A fixed restricting hole 17b such as an orifice for restricting the passage area to a predetermined amount is provided in the branch passage 16 of 23, and accordingly, the passage diameter of the capillary tube 17a of the first embodiment is larger than that of the capillary tube 17a. A large connecting pipe 160 is arranged.

  In the application example 2, the low-pressure refrigerant decompressed by the fixed throttle hole 17b formed in the branch passage 16 of the first connection block 23 is introduced into the right space 28 of the upper tank 18b of the second evaporator 18 through the connection pipe 160. Only the difference from Application Example 1 in FIGS. 13 to 15 is the same as Application Example 1 in FIGS. 13 to 15.

  By applying the present invention also to the application example 2 in FIGS. 16 to 18, the embodiment of the present invention can be obtained.

  Moreover, FIGS. 19-21 is the example 3 of application. In the application example 1 of FIGS. 13 to 15, the ejector 14 and the capillary tube 17 a are both arranged in a common tank, that is, the upper tank 18 b of the second evaporator 18, but the application examples of FIGS. 19 to 21 are used. 3, only the capillary tube 17 a is disposed in the upper tank 18 b of the second evaporator 18, while the ejector 14 is disposed in a separate dedicated tank 34.

  As the ejector 14 is removed from the upper tank 18b of the second evaporator 18, the second connection block 24 in the application example 1 of FIGS. 13 to 15 is eliminated, and instead, the longitudinal center in the upper tank 18b is removed. A partition plate 35 is arranged in the section, and the partition plate 35 partitions the internal space of the upper tank 18b to the left and right. The downstream end 17d of the capillary tube 17a passes through the partition plate 35 and communicates with the right space 28 in the upper tank 18b.

  As shown in FIG. 19, the separate tank 34 is disposed at an intermediate position between the upper tank 15b of the first evaporator 15 and the upper tank 18b of the second evaporator 18, and extends in the longitudinal direction of the tanks 15b and 18b. In this example, the separate tank 34 is formed integrally with the upper tanks 15b and 18b.

  As shown in FIG. 20, the ejector 14 and this separate cylindrical tank 34 extend to the back side (right side) of the partition plates 30 and 35 of both tanks 15b and 18b, and the outlet portion (diffuser of the diffuser) The outlet portion of the portion 14 d communicates with the right space 32 of the upper tank 15 b of the first evaporator 15 through a through hole (lateral hole) 34 a that penetrates the circumferential wall of the separate tank 34.

  Similarly, the refrigerant suction port 14b of the ejector 14 also communicates with the left space 27 of the upper tank 18b of the second evaporator 18 through a through hole (lateral hole) 34b penetrating the circumferential wall of another tank 34.

  Also in the application example 3 of FIGS. 19 to 21, the low-pressure refrigerant (gas-liquid two-phase refrigerant) flowing into the right space 28 from the downstream end 17d of the capillary tube 17a is a plurality of the right side of the heat exchange core 18a. Since the liquid flows directly into the tubes 21, the distribution of the liquid refrigerant to the plurality of tubes 21 becomes uneven.

  Therefore, the present invention can also be applied to the application example 3 of FIGS. 19 to 21 to form an embodiment of the present invention. That is, if the refrigerant | coolant storage board 75 is arrange | positioned in the right side space 28, distribution of the refrigerant | coolant with respect to the some tube 21 can be equalized similarly to 1st Embodiment.

  The application example 4 of FIGS. 22 to 24 is a modification of the application example 3 of FIGS. 19 to 21, and the capillary tube 17 a of the application example 3 of FIGS. 19 to 21 is abolished. The throttle hole 17b and the connecting pipe 160 are employed.

  That is, in the application example 4 of FIGS. 22 to 24, the fixed throttle hole 17 b is formed as the pressure reducing means in the branch passage 16 of the first connection block 23, and the second evaporator is connected to the downstream side of the fixed throttle hole 17 b through the connection pipe 160. The 18 upper tanks 18 b communicate with the right space 28.

  The present invention can also be applied to the application example 4 of FIGS. 22 to 24 to form an embodiment of the present invention.

  In the first embodiment and application examples 1 to 4, all employ the configuration in which the ejector 14 is disposed in the upper tank 18b of the second evaporator 18 or in another tank 34 adjacent to the upper tank 18b. In Application Example 5 of FIG. 25, the ejector 14 is configured in an external cassette unit 36 disposed outside the first and second evaporators 15 and 18.

  The cassette portion 36 forms an external member attached to the outside of the first and second evaporators 15 and 18, and is roughly divided into an ejector 14 portion, a lower case portion 37 that accommodates the ejector 14 portion, and The upper case part 38 is comprised.

  In the example of FIG. 25, the main body portion of the ejector 14 (portion in which the nozzle portion 14a is incorporated) is formed into a cylindrical shape extending in the vertical direction along one side surface of the first and second evaporators 15 and 18. Has been. Here, the main body portion of the ejector 14 may be formed of any metal such as aluminum or resin.

  Sealing materials S1 and S2 made of O-rings are arranged on the outer peripheral wall of the main body portion of the ejector 14. In addition, you may shape | mold the main-body part of the ejector 14 in shapes, such as a rectangular parallelepiped other than a column shape.

  A lower case portion 37 is fixed in advance to the side portions of the first and second evaporators 15 and 18. Specifically, the lower case portion 37 is formed in a vertically long rectangular parallelepiped shape that closes the bottom surface portion and opens the top surface portion. The material of the lower case portion 37 may be either a metal such as aluminum or a resin. And the lower case part 37 is being fixed to the side part of the 1st, 2nd evaporators 15 and 18 by means, such as screwing.

  Therefore, the ejector 14 portion is inserted into the lower case portion 37 from the upper surface opening of the lower case portion 37. Here, the upper part of the ejector 14, that is, the part above the refrigerant suction port 14 b of the ejector 14 (the inlet side part of the nozzle part 14 a) protrudes above the lower case part 37.

  After that, while fitting the upper case portion 38 to the upper protruding portion of the ejector 14, the upper case portion 38 is covered as a lid member on the upper surface opening of the lower case portion 37, and the upper case portion 38 and the lower case portion 37 are screwed together. Fasten together by means such as a stop.

  Thereby, the ejector 14 portion can be held and fixed in the lower case portion 37 and the upper case portion 38. In FIG. 25, since the air flow direction A is shown as reversed from FIG. 2 and the like, the left and right sides of the first and second evaporators 15 and 18 are also reversed as compared with FIG.

  The upper case portion 38 also integrally configures the function of the first connection block 23 in Application Examples 1 to 4. That is, the refrigerant inlet 25 and the refrigerant outlet 26 are adjacently formed in the upper case portion 38 in parallel. The refrigerant inlet 25 is branched into a main passage 25a and a branch passage 16 that are directed toward the inlet of the ejector 14 in the middle of the passage. A fixed throttle hole 17b is formed in the branch passage 16 as pressure reducing means. The fixed throttle hole 17b is the same as the fixed throttle hole 17b in Comparative Example 3 and Application Example 4.

  The main passage 25a is refracted in an L shape from the passage direction of the refrigerant inlet 25 and extends in the longitudinal direction (vertical direction) of the ejector 14, and the nozzle of the ejector 14 extends downward from above into the main passage 25a. A portion 14a, a mixing portion 14c, and a diffuser portion 14d are sequentially formed.

  The outlet portion of the ejector 14 (the outlet portion of the diffuser portion 14d) is positioned near the other end portion (lower end portion) of the ejector 14 in the longitudinal direction. The outlet portion of the ejector 14 is connected to one end portion of the connection pipe 39 through the communication hole 37 a of the lower case portion 37, and the other end portion of the connection pipe 39 is the right space portion of the upper tank 15 b of the first evaporator 15. 32.

  Further, the passage of the refrigerant outlet 26 of the upper case portion 38 is connected to the left space portion 31 of the upper tank 15 b of the first evaporator 15.

  The refrigerant suction port 14b of the ejector 14 is formed so as to penetrate the wall surface of the main body portion of the ejector 14 in the radial direction, and communicates with the downstream portion of the nozzle portion 14a of the ejector 14. The refrigerant suction port 14 b is connected to one end portion of the connection pipe 40 through the communication hole 38 a of the upper case portion 38, and the other end portion of the connection pipe 40 is connected to the left space 27 of the upper tank 18 b of the second evaporator 18. Connected.

  The outlet side of the fixed throttle hole 17 b of the branch passage 16 is connected to the right space 28 of the upper tank 18 b of the second evaporator 18 via the connection pipe 41.

  By connecting the passage of the external cassette part 36 and the four spaces 27, 28, 31, 32 on the left and right sides of the upper tanks 15b, 18b of the first and second evaporators 15, 18 as described above, The refrigerant after passing through the ejector 14 passes through the connection pipe 39 and then flows through the first evaporator 15 through the flow paths indicated by arrows a to e, and then flows from the refrigerant outlet 26 of the external cassette unit 36 to the external flow path (compression). Flow to the suction side).

  On the other hand, the refrigerant branched to the branch passage 16 side at the refrigerant inlet 25 and decompressed by the fixed throttle hole 17b passes through the connection pipe 41, and then passes through the second evaporator 18 in the flow paths indicated by arrows f to i. The flow reaches the left space 27 of the upper tank 18b. Then, the refrigerant is sucked from the left space 27 through the connection pipe 40 to the refrigerant suction port 14 b of the ejector 14.

  The present invention can also be applied to the application example 5 of FIG. 25 to form an embodiment of the present invention.

  In Application Example 5 of FIG. 25, a portion corresponding to the first connection block 23 is integrally formed with the upper case portion 38 of the external cassette unit 36. However, in Application Example 6 of FIG. It is separated from the external cassette portion 36 and configured as an independent part.

  In Application Example 6 of FIG. 26, the first connection block 23 is disposed on one (right) side of the left and right side surfaces of the first and second evaporators 15 and 18, and the other (left) side is disposed on the side surface. An external cassette unit 36 is arranged.

  The external cassette portion 36 is configured to hold and fix the ejector 14 portion in the lower case portion 37 and the upper case portion 38 as in Application Example 5 of FIG. However, in Application Example 6 of FIG. 26, the upper case portion 38, not the lower case portion 37, is fixed in advance to one side surface portion of the first and second evaporators 15 and 18.

  Then, the ejector 14 is inserted into the upper case portion 38 from the lower opening portion of the upper case portion 38, and thereafter, the lower case portion 37 is covered as a lid member on the lower opening portion of the upper case portion 38, and both upper and lower case portions are covered. 37 and 38 are fastened together by means such as screwing.

  Here, the assembly direction of the ejector 14 is the reverse direction of the application example 5 of FIG. 25, and the ejector 14 is placed so that the nozzle portion 14a side (inlet side) is downward and the diffuser portion 14d side (outlet side) is upward. It is assembled.

  The refrigerant suction port 14 b of the ejector 14 is connected to the left side portion of the lower tank 18 c of the second evaporator 18 through the communication hole 37 b of the lower case portion 37. The diffuser portion 14 d is connected to the left space portion 31 of the upper tank 15 b of the first evaporator 15 through the communication hole 38 b of the upper case portion 38.

  On the other hand, the refrigerant inlet 25 of the first connection block 23 is branched into a main passage 25a and a branch passage 16, and the main passage 25a is connected to a communication hole 37c of the lower case portion 37 of the external cassette portion 36 by a connection pipe 42. The communication hole 37 c communicates with the inlet 43 of the nozzle portion 14 a of the ejector 14.

  The branch passage 16 is connected to the right side portion of the lower tank 18c of the second evaporator 18 via a capillary tube 17a serving as a decompression means.

  In the second evaporator 18 of Application Example 6 in FIG. 26, the partition plate 35 of the upper tank 18b is eliminated, and instead, the partition plate 35a is disposed at the center in the longitudinal (left / right) direction of the lower tank 18c. The partition plate 35a partitions the inner space of the lower tank 18c to the left and right.

  For this reason, the low-pressure refrigerant that has passed through the capillary tube 17a flows through the second evaporator 18 through the refrigerant flow path indicated by arrows f to i, and then sucks the refrigerant from the ejector 14 through the communication hole 37b from the left side of the lower tank 18c. It is sucked into the mouth 14b.

  On the other hand, the refrigerant in the main passage 25a of the refrigerant inlet 25 passes through the connection pipe 42, flows into the inlet portion 43 of the ejector 14 of the external cassette portion 36 through the communication hole 37c, is decompressed by the nozzle portion 14a, and expands. The low-pressure refrigerant at the outlet of the ejector 14 flows into the left space 31 of the upper tank 15b of the first evaporator 15 through the communication hole 38b of the upper case 38.

  Thereafter, the low-pressure refrigerant flows in the first evaporator 15 through the refrigerant flow paths indicated by arrows a to d, and then flows to the refrigerant outlet 26 of the first connection block 23.

  The present invention can also be applied to the application example 6 of FIG. 26 to form an embodiment of the present invention.

(Second Embodiment)
In 1st Embodiment, although the edge part extended in the lamination direction of the tube 21 among the hole parts 75a of the refrigerant | coolant storage board 75 is formed in the waveform, in 2nd Embodiment, as shown to FIG. 27, FIG. The edge portion extending in the stacking direction of the tubes 21 in the hole portion 75a of the refrigerant storage plate 75 is linear, and the hole portion 75a is formed in a rectangular shape extending in the stacking direction of the tubes 21.

  Also in the second embodiment, the liquid refrigerant out of the gas-liquid two-phase refrigerant flowing into the lower space 70 from the capillary tube 17 a temporarily accumulates in the storage unit 76, and the liquid refrigerant overflowing from the storage unit 76 is stored in the refrigerant storage plate 75. It falls to the tube 21 side from the plurality of holes 75a. For this reason, the distribution of the liquid refrigerant to the plurality of tubes 21 can be made uniform.

(Third embodiment)
In the second embodiment, the hole 75a of the refrigerant storage plate 75 is formed in a rectangular shape extending in the stacking direction of the tubes 21, but in the third embodiment, as shown in FIGS. 29 and 30, the refrigerant storage plate 75 holes 75 a are formed in an elliptical shape extending in the stacking direction of the tubes 21.

  Also in the third embodiment, the liquid refrigerant out of the gas-liquid two-phase refrigerant flowing into the lower space 70 from the capillary tube 17 a temporarily accumulates in the storage unit 76, and the liquid refrigerant overflowing from the storage unit 76 is transferred to the refrigerant storage plate 75. It falls to the tube 21 side from the plurality of holes 75a. For this reason, the distribution of the liquid refrigerant to the plurality of tubes 21 can be made uniform.

(Fourth embodiment)
In 3rd Embodiment, although each hole 75a of the refrigerant | coolant storage plate 75 has overlapped with the inlet part 21a of the some tube 21, in 3rd Embodiment, as shown in FIG. The hole 75 a is superposed with only the inlet 21 a of one tube 21.

  In the fourth embodiment, the number of holes 75a is increased instead of reducing the diameter of the hole 75a in the longitudinal direction of the tube 21 compared to the third embodiment.

  More specifically, the intervals between the holes 75 a are made to coincide with the intervals between the tubes 21, and the holes 75 a are positioned above the inlet portion 21 a of the tube 21.

  In the fourth embodiment, the liquid refrigerant overflowing from the storage section 76 and falling from the plurality of holes 75a toward the tube 21 can be directly flowed into the tube 21.

  For this reason, the distribution of the liquid refrigerant to the plurality of tubes 21 can be satisfactorily made uniform.

(Fifth embodiment)
In each of the above embodiments, the refrigerant storage plate 75 is formed in a cross-sectional mountain shape, and the storage portion 76 is formed in the skirt portion 75d having a cross-sectional mountain shape. However, in the fifth embodiment, as shown in FIG. A concave portion 77a having a U-shaped cross section is formed in the plate 77, and a storage portion 78 is formed by the concave portion 77a.

  As shown in FIG. 32, the refrigerant storage plate 77 has a flat portion 77b extending from both end portions of the concave portion 77a having a U-shaped cross section toward the inner wall surface 60b extending in the vertical direction of the bottom side half-crack member 60 of the upper tank 18b. Is formed, and the front end surface 77c of the flat surface portion 77b is in contact with the inner wall surface 60b of the bottom surface side half crack member 60.

  On the flat surface portion 77b, a notch portion 77d facing the inner wall surface 60b of the bottom half crack member 60 is formed. Due to the space surrounded by the notch 77d and the inner wall surface 60b of the bottom half crack member 60, a hole 79 is formed for dropping the liquid refrigerant once stored in the storage part 78 in the recess 77a to the tube 21 side. Has been.

  In the sixth embodiment, the liquid refrigerant out of the gas-liquid two-phase refrigerant flowing from the capillary tube 17 a into the lower space 70 once accumulates in the storage part 78 of the refrigerant storage plate 77 and overflows from the storage part 78. Falls from the hole 79 toward the tube 21 as indicated by an arrow k.

  For this reason, distribution of the liquid refrigerant with respect to the plurality of tubes 21 can be made uniform as in the above embodiments.

(Sixth embodiment)
In the said 1st-4th embodiment, although the refrigerant | coolant storage board 75 is formed in cross-sectional mountain shape, and the storage part 76 is formed in the skirt part 75d of cross-sectional mountain shape, as shown in FIG. 33 in 6th Embodiment. In addition, the refrigerant storage plate 80 is formed in a flat plate shape having an inclined cross section, and a storage portion 81 is formed on the inclined lower side of the refrigerant storage plate 80.

  As shown in FIG. 33, both end portions 80 a of the cross section of the refrigerant storage plate 80 are in contact with the inner wall surface 60 b of the bottom surface side half crack member 60. Thus, a storage portion 81 for temporarily storing the liquid refrigerant is formed by the inclined lower side of the refrigerant storage plate 80 and the inner wall surface 60b of the bottom surface side half crack member 60.

  A cutout portion 80 b facing the inner wall surface 60 b of the bottom surface side half-crack member 60 is formed on the inclined lower side of the refrigerant storage plate 80. A space surrounded by the notch 80b and the inner wall surface 60b of the bottom half crack member 60 forms a hole 82 for dropping the liquid refrigerant once stored in the storage portion 81 to the tube 21 side.

  In the sixth embodiment, the liquid refrigerant of the gas-liquid two-phase refrigerant flowing into the lower space 70 from the capillary tube 17a temporarily accumulates in the storage unit 81, and the liquid refrigerant overflowing from the storage unit 81 is indicated by an arrow m. It falls from the hole 82 to the tube 21 side.

  For this reason, distribution of the liquid refrigerant with respect to the plurality of tubes 21 can be made uniform as in the above embodiments.

(Seventh embodiment)
In the first embodiment, the liquid receiver 12a is disposed on the outlet side of the radiator 12, and the expansion valve 13 is disposed on the outlet side of the liquid receiver 12a. In the embodiment, as shown in FIG. 34, an accumulator 50 that is a gas-liquid separator that separates the gas-liquid refrigerant and stores excess refrigerant as liquid is provided on the outlet side of the first evaporator 15. Is led out to the suction side of the compressor 11.

  In this accumulator-type cycle configuration, since the gas-liquid interface between the gas-phase refrigerant and the liquid-phase refrigerant is formed in the accumulator 50, the superheat degree control of the outlet refrigerant of the first evaporator 15 is expanded as in the first embodiment. There is no need to do this with the valve 13.

  Therefore, in the accumulator type cycle configuration, the liquid receiver 12a and the expansion valve 13 are eliminated, and the refrigerant inlet 25 of the integrated unit 20 may be directly connected to the outlet side of the radiator 12. Then, the refrigerant outlet 26 of the integrated unit 20 may be connected to the inlet side of the accumulator, and the outlet side of the accumulator may be connected to the suction side of the compressor 11.

(Eighth embodiment)
The eighth embodiment is a modification of the seventh embodiment. As shown in FIG. 35, the accumulator 50 is also integrally assembled as one element of the integrated unit 20, and the outlet portion of the accumulator 50 is integrated with the entire integrated unit 20. The refrigerant outlet 26 is configured.

(Ninth embodiment)
In the first to eighth embodiments, the branch passage 16 branched on the inlet side of the ejector 14 is connected to the refrigerant suction port 14b of the ejector 14, and the throttle mechanism 17 and the second evaporator 18 are arranged in the branch passage 16. In the ninth embodiment, as shown in FIG. 36, an accumulator 50 that forms a gas-liquid separator is provided on the outlet side of the first evaporator 15, and the liquid-phase refrigerant outlet portion 50a of the accumulator 50 is provided in the ninth embodiment. A branch passage 16 connected to the refrigerant suction port 14 b of the ejector 14 is provided, and a throttle mechanism 17 and a second evaporator 18 are arranged in the branch passage 16.

  In the ninth embodiment, the ejector 14, the first and second evaporators 15 and 18, the throttle mechanism 17, and the accumulator 50 constitute an integrated unit 20. Here, as a whole integrated unit 20, one refrigerant inlet 25 is provided on the inlet side of the ejector 14, and this refrigerant inlet 25 is connected to the outlet side of the radiator 12.

  Further, as a whole integrated unit 20, one refrigerant outlet 26 is provided at the gas-phase refrigerant outlet portion of the accumulator 50, and this refrigerant outlet 26 is connected to the suction side of the compressor 11.

(10th Embodiment)
In the first to ninth embodiments, each includes the first evaporator 15 connected to the outlet side of the ejector 14 and the second evaporator 18 connected to the refrigerant suction port 14b of the ejector 14. In the tenth embodiment, an integrated unit 20 is configured in an ejector refrigeration cycle 10 that includes only an evaporator 18 connected to the refrigerant suction port 14b of the ejector 14 as shown in FIG.

  The integrated unit 20 of the tenth embodiment includes an ejector 14, an evaporator 18, a throttle mechanism 17, and an accumulator 50. The unit as a whole has one refrigerant inlet 25 and one refrigerant outlet 26. ing. That is, the tenth embodiment corresponds to a configuration in which the first evaporator 15 of the ninth embodiment is eliminated.

(Eleventh embodiment)
In each of the first to ninth embodiments, the aperture mechanism 17 is also integrated in the integrated unit 20, but in the eleventh embodiment, the integrated unit 20 is connected to the first and second units as shown in FIG. It comprises the evaporators 15, 18 and the ejector 14, and the throttle mechanism 17 is provided separately from the integrated unit 20.

  In the eleventh embodiment, an example is shown in which no gas-liquid separator is disposed on either the cycle high-pressure side or the low-pressure side.

(Twelfth embodiment)
FIG. 39 shows a twelfth embodiment. In contrast to the eleventh embodiment, an accumulator 50 that forms a gas-liquid separator is provided on the outlet side of the first evaporator 15, and this accumulator 50 is integrated in the integrated unit 20. It has become. That is, in the twelfth embodiment, the ejector 14, the first and second evaporators 15 and 18, and the accumulator 50 constitute an integrated unit 20, and the throttle mechanism 17 is separated from the integrated unit 20 independently. Provided.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and various modifications can be made as described below.

  (1) In the first embodiment, when the members of the integrated unit 20 are assembled together, other members excluding the ejector 14, that is, the first evaporator 15, the second evaporator 18, the connection block 23, and the capillary tube 17a and the like are integrally brazed, but these members can be integrally assembled by using various fixing means such as screwing, caulking, welding, and adhesion in addition to brazing.

  Moreover, although screwing is illustrated as a fixing means of the ejector 14 in 1st Embodiment, means other than screwing can be used if it is a fixing means with no fear of thermal deformation. Specifically, the ejector 14 may be fixed using fixing means such as caulking or bonding.

  (2) In each of the above-described embodiments, the vapor compression subcritical cycle using a refrigerant such as a chlorofluorocarbon-based refrigerant or an HC-based refrigerant whose high pressure does not exceed the critical pressure has been described. However, carbon dioxide (CO2) is used as the refrigerant. Thus, the present invention may be applied to a vapor compression supercritical cycle using a refrigerant whose high pressure exceeds the critical pressure.

  However, in the supercritical cycle, the refrigerant discharged from the compressor is only dissipated in the supercritical state in the radiator 12, and does not condense. Therefore, in the liquid receiver 12a disposed on the high pressure side, the refrigerant gas-liquid separation action and The storage effect of the excess liquid refrigerant cannot be exhibited. Therefore, in the supercritical cycle, as shown in FIGS. 34 to 34, a configuration may be adopted in which an accumulator 50 that forms a low-pressure side gas-liquid separator is disposed on the outlet side of the first evaporator 15.

  (3) In the above-described embodiment, the throttle mechanism 17 is configured by the fixed throttle hole 17b such as the capillary tube 17a or the orifice, but the valve opening degree (passage throttle opening degree) of the throttle mechanism 17 is adjusted by an electric actuator. You may comprise the electric control valve made possible. Further, the throttle mechanism 17 may be configured by a combination of a fixed throttle and a solenoid valve such as the capillary tube 17a or the fixed throttle hole 17b.

  (4) In each of the above-described embodiments, the ejector 14 is exemplified by the fixed ejector having the nozzle portion 14a having a constant passage area. However, as the ejector 14, the variable ejector having the variable nozzle portion capable of adjusting the passage area. May be used.

  As a specific example of the variable nozzle portion, for example, a mechanism may be used in which a needle is inserted into the passage of the variable nozzle portion and the passage area is adjusted by controlling the position of the needle with an electric actuator.

  (5) In the first embodiment and the like, the example in which the present invention is applied to the refrigeration cycle for cooling the passenger compartment and cooling the inside of the refrigerator-freezer has been described. However, the first evaporator 15 having the refrigerant evaporation temperature on the high temperature side. Further, both the second evaporator 18 having the refrigerant evaporation temperature on the low temperature side may be used for cooling different areas in the vehicle interior (for example, the front seat side area in the vehicle interior and the rear seat side area in the vehicle interior).

  Further, both the first evaporator 15 having the refrigerant evaporation temperature on the high temperature side and the second evaporator 18 having the refrigerant evaporation temperature on the low temperature side may be used for cooling in the refrigerator-freezer. That is, the refrigeration chamber in the refrigerator-freezer is cooled by the first evaporator 15 having the refrigerant evaporation temperature on the high temperature side, and the freezer chamber in the refrigerator-freezer is cooled by the second evaporator 18 having the refrigerant evaporation temperature on the low temperature side. It may be.

  (6) In 1st Embodiment etc., the temperature type expansion valve 13 and the temperature sensing part 13a were comprised separately from the unit for ejector type refrigeration cycles. However, the temperature type expansion valve 13 and the temperature sensing part 13a may be integrally assembled to the ejector type refrigeration cycle unit. For example, the structure which accommodates the temperature type expansion valve 13 and the temperature sensing part 13a in the connection block 23 of the integrated unit 20 is employable. In this case, the refrigerant inlet 25 is located between the liquid receiver 12 a and the temperature type expansion valve 13, and the refrigerant outlet 26 is located between the passage portion where the temperature sensing unit 13 a is installed and the compressor 11. .

  (7) In each of the above-described embodiments, the refrigeration cycle for a vehicle has been described. However, the present invention is not limited to a vehicle and can be similarly applied to a refrigeration cycle for stationary use.

  (8) In the first embodiment, the downstream end 17d of the capillary tube 17a is horizontally inserted into the upper tank 18b, but the downstream end 17d of the capillary tube 17a is vertically inserted into the upper tank 18b. May be inserted.

  (9) In each of the above-described embodiments, the tank portions 15b, 15c, 18b, and 18c of the first evaporator 15 and the second evaporator 18 are arranged on both upper and lower sides of the first evaporator 15, that is, the first evaporator Although the evaporator 15 and the second evaporator 18 are arranged in the vertical direction, the first evaporator 15 and the second evaporator 18 may be arranged inclined with respect to the vertical direction.

  In this case, if the refrigerant storage plates 75, 77, 80 are inclined together with the first and second evaporators 15, 18, the liquid refrigerant tends to overflow from the storage portions 76, 78, 81, and the effect of storing the liquid refrigerant is reduced. Therefore, it is preferable to arrange the refrigerant storage plates 75, 77, and 80 at an angle similar to that of the above-described embodiments without inclining.

  (12) In each of the above-described embodiments, the example in which the present invention is applied to the evaporator 18 that is the heat absorption side heat exchanger of the refrigeration cycle has been described. However, the present invention is applied to heat exchangers for various uses. Applicable.

  For example, you may apply this invention to the condenser etc. which are the heat radiation side heat exchangers of a refrigerating cycle. Further, the present invention is applied to a heat exchanger in which hot water flows in an internal passage (a fluid passage corresponding to the tube 21 in each of the above embodiments), such as a warm water radiator for heating or a radiator for cooling an engine. May be.

  Further, the present invention can be similarly applied to a heat exchanger such as an engine oil cooler in which oil flows in the internal passage, or a heat exchanger in which cold water flows in the internal passage.

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 cross-sectional view of the evaporator tank part of the integrated unit of FIG. It is a longitudinal cross-sectional view of the evaporator tank part of the integrated unit of FIG. It is BB expanded sectional drawing in FIG. FIG. 3 is a perspective view of a connection block and an intervening plate in the integrated unit of FIG. 2. FIG. 3 is a perspective view of an ejector fixing plate in the integrated unit of FIG. 2. It is a perspective view of the up-and-down partition plate in the integrated unit of FIG. It is a perspective view of the spacer in the integrated unit of FIG. It is a perspective view of the refrigerant | coolant storage board in the integrated unit of FIG. It is a cross-sectional view of the lower space part of the integrated unit of FIG. It is a typical perspective view which shows the refrigerant | coolant flow path of the whole integrated unit 20 of FIG. 10 is a perspective view showing a schematic configuration of an integrated unit of Application Example 1. FIG. It is a cross-sectional view of the evaporator tank part of the integrated unit of FIG. It is a side view of the evaporator tank part of FIG. It is a perspective view which shows schematic structure of the integrated unit of the example 2 of application. It is a cross-sectional view of the evaporator tank part of the integrated unit of FIG. It is a side view of the evaporator tank part of FIG. It is a perspective view which shows schematic structure of the integrated unit of the application example 3. FIG. It is a longitudinal cross-sectional view of the evaporator tank part of the integrated unit of FIG. It is a cross-sectional view of the evaporator tank part of the integrated unit of FIG. It is a perspective view which shows schematic structure of the integrated unit of the example 4 of application. It is a longitudinal cross-sectional view of the evaporator tank part of the integrated unit of FIG. It is a side view of the evaporator tank part of FIG. It is a perspective view which shows schematic structure of the integrated unit of the application example 5, and combines sectional drawing of an external cassette part. It is a perspective view which shows schematic structure of the integrated unit of the application example 6, and combines sectional drawing of an external cassette part. It is a perspective view of the refrigerant | coolant storage board by 2nd Embodiment. It is a cross-sectional view of the lower space portion of the integrated unit according to the second embodiment. It is a perspective view of the refrigerant storage board by a 3rd embodiment. It is a cross-sectional view of the lower space part of the integrated unit by 3rd Embodiment. It is a cross-sectional view of the lower space part of the integrated unit by 4th Embodiment. It is a longitudinal cross-sectional view of the evaporator tank part of the integrated unit by 5th Embodiment. It is a longitudinal cross-sectional view of the evaporator tank part of the integrated unit by 6th Embodiment. It is a refrigerant circuit figure of the ejector type refrigeration cycle for vehicles by a 7th embodiment. It is a refrigerant circuit figure of the ejector type refrigeration cycle for vehicles by an 8th embodiment. It is a refrigerant circuit figure of the ejector type refrigeration cycle for vehicles by a 9th embodiment. It is a refrigerant circuit figure of the ejector type refrigeration cycle for vehicles by a 10th embodiment. It is a refrigerant circuit figure of the ejector type refrigeration cycle for vehicles by an 11th embodiment. It is a refrigerant circuit figure of the ejector type refrigeration cycle for vehicles by a 12th embodiment.

Explanation of symbols

18b ... upper tank (tank), 21 ... tube (fluid passage),
21a ... Inlet part, 75 ... Refrigerant storage plate (storage member), 75a ... Hole part, 75d ... Bottom part,
76: Storage part, θ: Bending angle.

Claims (7)

A plurality of fluid passages (21) through which a heat exchange fluid including at least a liquid phase fluid flows;
A tank (18b) disposed above the inlet portions (21a) of the plurality of fluid passages (21) and distributing heat exchange fluid flow to the plurality of fluid passages (21),
Storage members (75, 77, 80) for temporarily storing the liquid phase fluid flowing into the tank (18b) are disposed inside the tank (18b) and above the inlet (21a). And
The heat exchanger, wherein the liquid phase fluid overflowing from the storage member (75, 77, 80) falls to the inlet (21a) side. The storage member (75) is formed in a cross-sectional mountain shape,
A valley-shaped storage part (76) is formed by the skirt part (75d) having the mountain-shaped cross section and the inner wall surface (60b) extending in the vertical direction of the tank (18b),
Furthermore, a hole (75a) is formed in the top of the mountain-shaped cross section of the storage member (75),
The liquid phase fluid temporarily accumulates in the reservoir (76), and the liquid phase fluid accumulated in the reservoir (76) falls through the hole (75a). The heat exchanger according to 1. The heat exchanger according to claim 2, wherein a bending angle (θ) of the cross-sectional mountain shape is set in a range of 30 degrees or more and 170 degrees or less. The heat exchanger according to claim 2 or 3, wherein the hole portion (75a) is arranged so as to overlap with the inlet portion (21a). The heat exchanger according to any one of claims 2 to 4, wherein an edge of the hole (75a) is formed in a wave shape. The edge of the hole (75a) is formed in a wave shape,
The hole (75a) is arranged such that a top portion (75c) of the corrugated shape that is recessed to the outside of the hole (75a) overlaps with the inlet portion (21a). The heat exchanger according to claim 2 or 3. The refrigerant was sucked from the refrigerant suction port (14b) by the high-speed refrigerant flow ejected from the nozzle part (14a), and sucked from the refrigerant jetted from the nozzle part (14a) and the refrigerant suction port (14b). An ejector (14) that mixes and discharges the refrigerant;
A first evaporator (15) for evaporating the refrigerant discharged from the ejector (14);
A second evaporator (18) for evaporating the refrigerant sucked into the refrigerant suction port (14b),
The said 2nd evaporator (18) is comprised by the heat exchanger as described in any one of Claim 1 thru | or 6, The unit for ejector type refrigeration cycles characterized by the above-mentioned.

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