JP6323313B2 - Evaporator unit - Google Patents

Description

  The present invention relates to an evaporator unit used in an ejector refrigeration cycle.

  2. Description of the Related Art Conventionally, an ejector refrigeration cycle that is a vapor compression refrigeration cycle apparatus including an ejector as refrigerant decompression means is known.

  In this type of ejector refrigeration cycle, the pressure of the refrigerant sucked into the compressor can be increased by the pressurizing action of the ejector. Therefore, it is possible to reduce the power consumption of the compressor and improve the coefficient of performance (COP) of the cycle, compared to a general refrigeration cycle apparatus in which the refrigerant evaporation pressure in the evaporator and the pressure of the suction refrigerant are equal.

  Furthermore, Patent Document 1 discloses an evaporator unit used in an ejector refrigeration cycle. This evaporator unit is obtained by integrating (unitizing) two ejectors arranged in series in the flow direction of the ejector and the blown air.

  More specifically, in the evaporator unit of Patent Document 1, the refrigerant flowing out from the leeward evaporator disposed on the leeward side of the blown air is guided to the refrigerant suction port of the ejector, and is increased by the booster (diffuser part) of the ejector. The pressurized refrigerant is caused to flow into an upwind evaporator disposed on the upwind side of the blown air flow. Thereby, the temperature difference of the refrigerant | coolant evaporation temperature in both evaporators and blowing air is ensured, and it is trying to cool blowing air efficiently.

JP 2011-220551 A

  By the way, in an ejector applied to an ejector-type refrigeration cycle, the refrigerant is sucked from the refrigerant suction port by the suction action of the high-speed jet refrigerant jetted from the nozzle section, and the mixed refrigerant of the jet refrigerant and the sucked refrigerant is diffused in the diffuser section. Spill from. Therefore, in the evaporator unit of Patent Document 1, the refrigerant flow rate G (mass flow rate) of the outflow refrigerant flowing through the windward evaporator is larger than the refrigerant flow rate Ge (mass flow rate) of the suction refrigerant flowing through the leeward evaporator. Become.

  For this reason, in the evaporator unit of patent document 1, the pressure loss which arises when an outflow refrigerant | coolant passes an upwind evaporator tends to become large. And if the pressure loss generated when the effluent refrigerant passes through the windward evaporator becomes large, the pressure of the refrigerant sucked into the compressor will decrease, so the above-described ejector refrigeration cycle is configured. The COP improvement effect due to this cannot be obtained sufficiently.

  In view of the above points, an object of the present invention is to reduce a pressure loss that occurs when a refrigerant circulates in an evaporator unit used in an ejector refrigeration cycle.

The present invention has been devised in order to achieve the above object. In the invention according to claim 1, the nozzle portion (15a) for depressurizing the refrigerant, and the high speed injected from the nozzle portion (15a) are provided. The refrigerant suction port (15c) for sucking the refrigerant by the suction action of the jet refrigerant and the pressure increasing unit (15d) for increasing the pressure by mixing the jet refrigerant and the suction refrigerant sucked from the refrigerant suction port (15c) are formed. An ejector (15) having a body part (15b), an upwind evaporator (17) arranged on the windward side of the flow of air blown into the space to be cooled, and air to the upwind evaporator (17) A leeward evaporator (18) disposed on the leeward side of the flow of
The upwind evaporator (17) is provided with a first outflow side heat exchange section (17a) that exchanges heat with the air to evaporate the outflow refrigerant flowing out from the pressure increasing section (15d), and evaporates the downwind evaporator (17d). 18) includes a second outflow side heat exchange section (18a) for exchanging heat with the air to evaporate the outflow refrigerant, and a suction side for evaporating the refrigerant sucked into the refrigerant suction port (15c) with heat exchange with air. A heat exchange section (18b) is provided;
The first outflow side heat exchange section (17a) and the second outflow side heat exchange section (18a) are characterized by an evaporator unit connected in parallel to the flow of the outflow refrigerant.

  According to this, the 1st outflow side heat exchange part (17a) and the 2nd outflow side heat exchange part (18a) are connected in parallel with respect to the flow of the outflow refrigerant which flowed out from the pressurization part (15d). Therefore, the outflow refrigerant can be caused to flow into both the first outflow side heat exchange section (17a) and the second outflow side heat exchange section (18a).

  Therefore, the passage cross-sectional area of the refrigerant flow path through which the outflow refrigerant flows is compared with the case where the outflow refrigerant flows into one of the first outflow side heat exchange section (17a) and the second outflow side heat exchange section (18a). Can be enlarged. As a result, it is possible to reduce the pressure loss that occurs when the outflow refrigerant having a larger flow rate than the suction refrigerant flows through the evaporator unit (20).

In the evaporator unit having the above characteristics, at least a part of the first outflow side heat exchanging portion (17a) and the second outflow side heat exchanging portion (18a) is superposed when viewed from the air flow direction. Are located in
The first outflow side heat exchanging portion (17a) and the second outflow side heat exchanging portion (18a) communicate with each other at the refrigerant inlet sides and with each other at the refrigerant outlet sides. It may be connected in parallel to the flow of.

  According to this, since the first outflow side heat exchange section (17a) and the second outflow side heat exchange section (18a) can be arranged close to each other, the outflow refrigerant is supplied to the first outflow side heat exchange section (17a) and the second outflow heat exchange section (17a). 2 It is possible to reduce the pressure loss of the refrigerant flow path leading to the outflow side heat exchange section (18a). Therefore, the pressure loss that occurs when the refrigerant flows through the evaporator unit (20) can be more effectively reduced.

In the evaporator unit having the above characteristics, more specifically, the windward evaporator (17) includes a plurality of windward tubes (71) through which the refrigerant flows and a refrigerant that flows through the plurality of windward tubes (71). The windward side tanks (72, 73) for collecting or distributing the windward side tanks (72, 73) are formed in a shape extending in the stacking direction of the plurality of windward side tubes (71), and the leeward side The evaporator (18) has a plurality of leeward tubes (81) for circulating the refrigerant and a leeward tank (82, 83) for collecting or distributing the refrigerants flowing through the plurality of leeward tubes (81). The leeward tanks (82, 83) are formed in a shape extending in a direction parallel to the leeward tanks (72, 73) in the stacking direction of the plurality of leeward tubes (81),
Further, in the windward evaporator (17), a refrigerant obtained by combining the refrigerant that has flowed out of the first outflow side heat exchange section (17a) and the refrigerant that has flowed out of the second outflow side heat exchange section (18a) is combined with air. The 3rd outflow side heat exchange part (17b) which is made to heat-exchange and evaporate may be provided.

  In this way, the windward evaporator (17) and the leeward evaporator (18) are constituted by so-called tank-and-tube heat exchangers, so that the first outflow is caused by a part of the plurality of windward tubes (71). A side heat exchange part (17a) can be comprised, and a 2nd outflow side heat exchange part (18a) can be comprised by a part of several leeward side tube (81). And the flow-path structure by which a 1st outflow side heat exchange part (17a) and a 2nd outflow side heat exchange part (18a) are connected in parallel with respect to the flow of an outflow refrigerant | coolant can be implement | achieved easily.

  Furthermore, the number of the windward side tubes (71) constituting the first outflow side heat exchange part (17a), the number of the windward side tubes (71) constituting the third outflow side heat exchange part (17b), the second outflow side By changing the number of leeward side tubes (81) constituting the heat exchange part (18a) and the number of leeward side tubes (81) constituting the suction side heat exchange part (18b), each heat exchange part (17a The heat exchange area of 18b) and the passage cross-sectional areas (AT1, AT2, AT3) of the refrigerant flow paths in the heat exchange portions (17a ... 18b) can be easily changed.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a whole block diagram of the ejector-type refrigerating cycle of 1st Embodiment. It is an external appearance perspective view of the evaporator unit of 1st Embodiment. It is a typical disassembled perspective view of the storage tank, the upper windward tank, and the upper leeward tank of the evaporator unit of the first embodiment. It is IV-IV expanded sectional drawing of FIG. It is VV expanded sectional drawing of FIG. It is VI-VI expanded sectional drawing of FIG. It is a VII-VII expanded sectional view of Drawing 3. It is a typical disassembled perspective view of the joint part of the evaporator unit of 1st Embodiment. It is an enlarged plan view of the 2nd plate of the joint part of the evaporator unit of a 1st embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the evaporator unit of 1st Embodiment. It is a graph which shows the change of the cooling performance improvement degree with respect to the change of a leeward side heat exchange part ratio. It is a graph which shows the change of the power consumption reduction effect with respect to the change of a leeward side heat exchange part ratio. It is a graph which shows the change of the cooling performance with respect to the change of a leeward side heat exchange part ratio. It is a graph which shows the change of the temperature difference with respect to the change of a leeward side heat exchange part ratio. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the evaporator unit of 2nd Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the evaporator unit of 3rd Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the evaporator unit of 4th Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the evaporator unit of 5th Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the evaporator unit of 6th Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the evaporator unit of 7th Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the evaporator unit of 8th Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the evaporator unit of 9th Embodiment. It is explanatory drawing for demonstrating the refrigerant | coolant flow in the evaporator unit of 10th Embodiment.

(First embodiment)
Hereinafter, the first embodiment of the present invention will be described with reference to FIGS. The evaporator unit 20 of the present embodiment is applied to a vapor compression refrigeration cycle apparatus including an ejector as a refrigerant decompression unit, that is, an ejector refrigeration cycle 10 as shown in the overall configuration diagram of FIG. Furthermore, this ejector type refrigeration cycle 10 is applied to a vehicle air conditioner, and fulfills a function of cooling blown air blown into a vehicle interior that is a space to be cooled.

  Further, the ejector refrigeration cycle 10 of the present embodiment employs an HFC-based refrigerant (specifically, R134a) as the refrigerant, and constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the refrigerant critical pressure. doing. Of course, an HFO refrigerant (specifically, R1234yf) or the like may be adopted as the refrigerant. Furthermore, refrigeration oil for lubricating the compressor 11 is mixed in the refrigerant, and a part of the refrigeration oil circulates in the cycle together with the refrigerant.

  Of the constituent devices of the ejector refrigeration cycle 10, the compressor 11 sucks the refrigerant and compresses and discharges the refrigerant until it becomes a high-pressure refrigerant. Specifically, the compressor 11 of the present embodiment is an electric compressor configured by housing a fixed capacity type compression mechanism and an electric motor that drives the compression mechanism in one housing.

  As this compression mechanism, various compression mechanisms such as a scroll-type compression mechanism and a vane-type compression mechanism can be employed. Further, the operation (rotation speed) of the electric motor is controlled by a control signal output from an air conditioning control device (not shown), and either an AC motor or a DC motor may be adopted.

  The refrigerant inlet side of the condenser 12 a of the radiator 12 is connected to the discharge port of the compressor 11. The radiator 12 is a heat-dissipating heat exchanger that radiates and cools the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and the outside air (outside air) blown by the cooling fan 12c. is there.

  More specifically, the heat radiator 12 exchanges heat between the high-pressure gas-phase refrigerant discharged from the compressor 11 and the outside air blown from the cooling fan 12c, and dissipates the high-pressure gas-phase refrigerant to condense it. And a receiver unit 12b configured to have a receiver unit 12b that separates gas-liquid refrigerant flowing out of the condensing unit 12a and stores excess liquid-phase refrigerant.

  The cooling fan 12c is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the air conditioning control device.

  An inlet side of the temperature type expansion valve 13 is connected to the refrigerant outlet of the receiver unit 12 b of the radiator 12. The temperature type expansion valve 13 is a refrigerant decompression unit that decompresses the refrigerant that has flowed out from the receiver unit 12 b of the radiator 12. Furthermore, the temperature type expansion valve 13 of the present embodiment adjusts the refrigerant flow rate so that the superheat degree of the evaporator unit 20 outlet side refrigerant approaches a predetermined reference superheat degree.

  Such a temperature type expansion valve 13 includes a temperature sensing part having a displacement member (diaphragm) that is displaced according to the temperature and pressure of the refrigerant flowing out of the evaporator unit 20, and according to the displacement of the displacement member. It is possible to employ one in which the valve opening degree (refrigerant flow rate) is adjusted by a mechanical mechanism so that the superheat degree of the refrigerant on the outlet side of the evaporator unit 20 approaches the reference superheat degree.

  The outlet of the temperature type expansion valve 13 is connected to the refrigerant inlet 24 a side provided in the joint portion 24 of the evaporator unit 20. The evaporator unit 20 is obtained by integrating (unitizing) the cycle constituent devices surrounded by a broken line in FIG. More specifically, the evaporator unit 20 is obtained by integrating the upstream branching section 14, the ejector 15, the downstream branching section 16, the windward evaporator 17, the leeward evaporator 18, the fixed throttle 19, and the like. .

  First, each component apparatus which comprises the evaporator unit 20 is demonstrated. The upstream branching portion 14 branches the flow of the refrigerant that has flowed in from the outside through the refrigerant inlet 21a, and flows one branched refrigerant out to the inlet side of the nozzle portion 15a of the ejector 15 and the other branched The refrigerant flows out to the inlet side of the fixed throttle 19.

  The ejector 15 functions as a refrigerant decompression unit that decompresses one of the refrigerant branched at the upstream branching section 14 until it becomes a low-pressure refrigerant, and sucks the refrigerant by a suction action of a refrigerant flow injected at a high speed ( It functions as a refrigerant circulation means (refrigerant transportation means) to be circulated by transportation.

  More specifically, the ejector 15 includes a nozzle portion 15a and a body portion 15b. The nozzle portion 15a is formed of a substantially cylindrical metal (for example, a stainless alloy) that gradually tapers in the refrigerant flow direction. It expands under reduced pressure entropy.

  In the refrigerant passage formed inside the nozzle portion 15a, a throat portion having the smallest refrigerant passage area is formed, and further, the refrigerant passage area gradually increases from the throat portion toward the refrigerant injection port for injecting the refrigerant. A divergent section is formed. That is, the nozzle portion 15a is configured as a Laval nozzle.

  Further, in the present embodiment, the nozzle portion 15a is set such that the flow rate of the refrigerant injected from the refrigerant injection port is equal to or higher than the speed of sound. Of course, you may comprise the nozzle part 15a with a tapered nozzle.

  The body portion 15b is formed of a substantially cylindrical metal (for example, aluminum alloy), functions as a fixing member that supports and fixes the nozzle portion 15a therein, and forms an outer shell of the ejector 15. More specifically, the nozzle portion 15a is fixed by press-fitting so as to be housed inside the longitudinal end of the body portion 15b. Therefore, the refrigerant does not leak from the fixed portion (press-fit portion) between the nozzle portion 15a and the body portion 15b.

  In addition, a refrigerant suction port 15c provided so as to penetrate the inside and outside of the outer peripheral surface of the body portion 15b and communicate with the refrigerant injection port of the nozzle portion 15a is provided in a portion corresponding to the outer peripheral side of the nozzle portion 15a. Is formed. The refrigerant suction port 15c is a through hole that sucks the refrigerant that has flowed out from the suction side heat exchange unit 18b of the leeward evaporator 18, which will be described later, into the inside of the ejector 15 by the suction action of the jet refrigerant injected from the nozzle unit 15a. is there.

  Further, inside the body portion 15b, a suction passage that guides the suction refrigerant sucked from the refrigerant suction port 15c to the refrigerant injection port side of the nozzle portion 15a, and the inside of the ejector 15 through the suction passage from the refrigerant suction port 15c. A diffuser portion 15d is formed as a pressure increasing portion for mixing and increasing the pressure of the suctioned refrigerant and the injected refrigerant.

  The suction passage is formed by a space between the outer peripheral side around the tapered tip of the nozzle portion 15a and the inner peripheral side of the body portion 15b, and the refrigerant passage area of the suction passage is directed toward the refrigerant flow direction. It is gradually shrinking. Thereby, the flow velocity of the suction refrigerant flowing through the suction passage is gradually increased, and the energy loss (mixing loss) when the suction refrigerant and the injection refrigerant are mixed in the diffuser portion 15d is reduced.

  The diffuser portion 15d is disposed so as to be continuous with the outlet of the suction passage, and is formed so that the refrigerant passage area gradually increases. Thereby, while mixing the injected refrigerant and the suction refrigerant, the function of decelerating the flow rate and increasing the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant, that is, the function of converting the velocity energy of the mixed refrigerant into pressure energy Fulfill.

  More specifically, the cross-sectional shape of the inner peripheral wall surface of the body portion 15b that forms the diffuser portion 15d of the present embodiment is formed by combining a plurality of curves. And since the degree of spread of the refrigerant passage cross-sectional area of the diffuser portion 15d gradually increases in the refrigerant flow direction and then decreases again, the refrigerant can be increased in an isentropic manner.

  A downstream branching portion 16 is disposed at the outlet of the diffuser portion 15d. The downstream branching portion 16 branches the flow of the effluent refrigerant that has flowed out of the diffuser portion 15d, and causes the branched one effluent refrigerant to flow out to the first outflow side heat exchange portion 17a side of the windward evaporator 17, and is branched. The other refrigerant is allowed to flow out to the second outflow side heat exchange section 18a side of the leeward evaporator 18.

  The windward side evaporator 17 and the leeward side evaporator 18 exchange the heat between the blown air blown from the blower fan 20a toward the vehicle interior and the refrigerant, evaporate the refrigerant, and exhibit the endothermic effect, thereby generating the blown air. It is a heat exchanger for endothermic cooling. Further, the windward side evaporator 17 and the leeward side evaporator 18 are arranged in series with respect to the air flow of the blown air, and the leeward side evaporator 18 is the air of the blown air with respect to the windward side evaporator 17. Located on the leeward side of the flow.

  The upwind evaporator 17 includes a first outflow side heat exchange unit 17a that evaporates one outflow refrigerant branched in the downstream side branch unit 16, and a refrigerant that flows out of the first outflow side heat exchange unit 17a and the downwind A third outflow side heat exchanging portion 17b that evaporates the refrigerant that merges with the refrigerant that has flowed out from the second outflow side heat exchanging portion 18a provided in the side evaporator 18 is provided.

  In the leeward evaporator 18, the second outflow side heat exchange unit 18 a that evaporates the other outflow refrigerant branched by the downstream side branch unit 16, and the refrigerant depressurized by the fixed throttle 19 are evaporated to eject the ejector. A suction side heat exchanging portion 18b is provided to flow out to the refrigerant suction port 15c side. The blower fan 20a is an electric blower in which the rotation speed (the amount of blown air) is controlled by a control voltage output from the air conditioning control device.

  The fixed throttle 19 is a pressure reducing means for reducing the pressure of the other refrigerant branched at the upstream branching section 14 until it becomes a low pressure refrigerant. The refrigerant outlet of the third outflow side heat exchange part 17b of the windward evaporator 17 is connected to the inlet side of the compressor 11 via the refrigerant outlet 24b provided in the joint part 24 of the evaporator unit 20. Yes.

  Next, the integration of the components constituting the evaporator unit 20 will be described with reference to FIGS. In addition, the up and down arrows in FIG. 2 indicate the up and down directions in a state where the evaporator unit 20 is mounted on the vehicle.

  First, the windward side evaporator 17 and the leeward side evaporator 18 of this embodiment are comprised with what is called a tank and tube type heat exchanger. That is, the windward evaporator 17 is connected to both ends of the plurality of windward tubes 71 for circulating the refrigerant and the plurality of windward tubes 71 and collects or distributes the refrigerant flowing through the windward tube 71. Upwind tanks 72 and 73 are provided.

  The windward tube 71 is made of a metal having excellent heat conductivity (in this embodiment, the same aluminum alloy as the body portion 15b of the ejector 15). Furthermore, the windward side tube 71 is comprised by the flat tube by which the cross-sectional shape perpendicular | vertical to the flow direction (longitudinal direction of the windward side tube 71) of the refrigerant | coolant which distribute | circulates inside was formed in flat shape.

  Each of the windward tubes 71 is laminated and arranged with a certain interval so that the flat surfaces (flat surfaces) of the outer surfaces are parallel to each other. Thus, an air passage through which the blown air flows is formed between the adjacent windward tubes 71. In other words, in the windward evaporator 17, a plurality of windward tubes 71 are stacked to form a heat exchange part (heat exchange core part) that exchanges heat between the refrigerant and the blown air.

  Further, fins 74 that promote heat exchange between the refrigerant and the blown air are disposed in the air passage formed between the adjacent windward tubes 71. The fins 74 are corrugated fins formed by bending a thin plate material of the same material as the windward tube 71 into a wave shape, and the tops thereof are brazed and joined to the flat surface of the windward tube 71.

  The windward side tanks 72 and 73 are formed of a bottomed cylindrical member made of the same material as the windward side tube 71. More specifically, the windward tanks 72 and 73 are formed in a shape extending in the stacking direction of the windward tubes 71. Inside the windward tanks 72 and 73, a distribution space for distributing the refrigerant to each windward tube 71 and a collecting space for collecting the refrigerant flowing out of each windward tube 71 are formed. .

  In the following description, for clarification of the description, among the windward tanks, the tank disposed on the upper side in the vertical direction is referred to as the upper windward tank 72, and the tank disposed on the lower side in the vertical direction is referred to as the lower windward side. It is described as a tank 73.

  The basic configuration of the leeward evaporator 18 is the same as that of the leeward evaporator 17. Accordingly, the leeward evaporator 18 is connected to both ends of the plurality of leeward tubes 81, fins 74, and the plurality of leeward tubes 81 that circulate the refrigerant, and collects or distributes the refrigerant that flows through the leeward tubes 81. A pair of leeward tanks (specifically, an upper leeward tank 82 disposed on the upper side in the vertical direction and a lower leeward tank 83 disposed on the lower side in the vertical direction).

  The leeward side tube 81 is a flat tube exactly the same as the leeward side tube 71. In this embodiment, the common use of such components reduces the manufacturing cost of the evaporator unit 20 as a whole.

  Furthermore, in this embodiment, at least a part of the upper windward tank 72 of the windward evaporator 17 and the upper windward tank 82 of the leeward evaporator 18 are formed of the same member, and the lower windward tank 73 and the lower At least a part of the leeward tank 83 is formed of the same member.

  Then, the windward side evaporator 17 and the leeward side evaporator 18 are integrated by brazing and joining the windward side tube 71, the leeward side tube 81, the windward side tanks 72 and 73, the leeward side tanks 82 and 83, the fins 74, and the like. It has become.

  In FIG. 2, for the sake of illustration, a part of the windward evaporator 17 (windward tube 71 and upper windward tank 72) is indicated by parentheses in the corresponding structure of the leeward evaporator 18. Is shown. Further, in FIG. 2, the fins 74 are illustrated only in a part of the leeward evaporator 18 for clarity of illustration, but the fins 74 are disposed between the adjacent windward tubes 71 in the windward evaporator 17. The leeward evaporator 18 is disposed over substantially the entire area between the adjacent leeward tubes 81.

  Next, the ejector 15 is housed in the housing tank 23 formed of a bottomed cylindrical member extending in parallel with the longitudinal direction of the upper windward tank 72 and the upper windward tank 82. The storage tank 23 is disposed in a valley between the upper windward tank 72 and the upper leeward tank 82 when viewed from the longitudinal direction.

  The storage tank 23 is made of the same material as the upper windward tank 72 and the upper windward tank 82. Further, the outer peripheral side surface of the storage tank 23 is brazed to the outer peripheral side surface of the upper windward tank 72 and the outer peripheral side surface of the upper leeward tank 82, so that the ejector 15 and the storage tank 23 are connected to the windward evaporator 17. And integrated into the leeward evaporator 18.

  Further, by brazing and joining the outer peripheral wall surface of the ejector 15 to the inner peripheral wall surface of the storage tank 23, the internal space of the storage tank 23 is, as shown in FIG. 3, the ejector inlet side space 23a and the ejector suction side space 23b. The ejector outlet side space 23c is divided into three spaces.

  The ejector inlet side space 23a shown in FIG. 4 is a space disposed on the upstream side of the refrigerant flow of the nozzle portion 15a (upstream side of the nozzle portion 15a), and is one end of the storage tank 23 with respect to the nozzle portion 15a of the ejector 15. Formed on the side. Further, the ejector inlet side space 23 a communicates with a refrigerant inlet 24 a provided in the joint portion 24.

  The ejector outlet side space 23c shown in FIGS. 6 and 7 is a space into which the refrigerant flowing out from the diffuser portion 15d flows, and is formed on the other end side of the storage tank 23 with respect to the diffuser portion 15d of the ejector 15. .

  The ejector suction side space 23b shown in FIG. 5 is a space into which the refrigerant sucked into the refrigerant suction port 15c flows, and is formed on the outer peripheral side of the ejector 15. Therefore, the ejector suction side space 23b is arranged so as to be sandwiched between the ejector inlet side space 23a and the ejector outlet side space 23c from both longitudinal ends of the storage tank 23. Further, the refrigerant suction port 15c of the ejector 15 is opened in the ejector suction side space 23b.

  Further, inside each tank 72, 82, 83, a partition member 821 for partitioning the internal space of each tank 72, 82, 83, and each separator 721, 822, 831, 832 are brazed and joined. .

  More specifically, inside the upper leeward tank 82, a partition member 821 that partitions the internal space of the upper leeward tank 82 into three spaces, and an internal space that extends perpendicularly to the longitudinal direction of the upper leeward tank 82. An upper leeward separator 822 is arranged to partition The partition member 821 is composed of a partition plate extending in the longitudinal direction of the upper leeward tank 82 and three partition plates extending perpendicularly to the longitudinal direction.

  As a result, as shown in FIG. 3, the internal space of the upper leeward tank 82 is divided into the one end side space 82a on the upper leeward side, the tube side space 82b, the anti-tube side space 82c, and the other end side space 82d on the upper leeward side. It is divided into four spaces.

  The one end side space 82a on the upper leeward side shown in FIG. 4 is formed on one end side of the upper leeward side tank 82 (the side on which the ejector inlet side space 23a is formed). Furthermore, the one end side space 82a on the upper leeward side communicates with the ejector inlet side space 23a.

  At this time, in the present embodiment, burring is performed on the opening edge portion of the communication hole provided in the portion of the storage tank 23 where the ejector inlet side space 23a is formed, thereby projecting toward the upper leeward tank 82. A burring part (protrusion part) is formed. The burring portion is brazed and joined in a state where the burring portion is fitted in a communication hole provided in a portion of the upper leeward tank 82 where the one end side space 82a is formed.

  This prevents positional displacement of the storage tank 23 and the upper leeward tank 82 during brazing and secures a brazing margin by the burring portion, thereby realizing good brazing. Moreover, as shown in FIGS. 5-7, the burring part is similarly formed in the opening edge part of the communicating hole of any one tank also about the communicating part of other tanks.

  A fixed throttle 19 that functions as an orifice is disposed in a portion of the ejector 15 that forms the ejector inlet side space 23 a and communicates with the one end side space 82 a of the upper leeward tank 82.

Furthermore, in this embodiment, the refrigerant flow rate (mass flow rate) flowing from the ejector inlet side space 23a into the nozzle portion 15a is defined as the nozzle portion side flow rate Gnoz, and the refrigerant flow rate (mass flow rate) flowing into the fixed throttle 19 is defined as the suction flow rate Ge. Then, the flow characteristics of the nozzle portion 15 and the fixed throttle 19 are determined so as to satisfy the following formula F1.
Ge / (Ge + Gnoz) ≦ 0.7 (F1)
Here, the refrigerant flowing out from the diffuser portion 15d of the ejector 15 is a refrigerant obtained by mixing the injection refrigerant injected from the nozzle portion 15 and the suction refrigerant sucked from the refrigerant suction port 15c.

  Therefore, the denominator (Ge + Gnoz) in the formula F1 is equal to the refrigerant flow rate (outflow flow rate) G of the outflow refrigerant flowing out from the diffuser portion 15d. Further, in the present embodiment, the flow rate characteristics of the nozzle portion 15 and the fixed throttle 19 are set so that the flow rate ratio Ge / G is 0.5 or less, more preferably, the flow rate ratio Ge / G approaches 0.3. Is determined.

  The other leeward side space 82d on the upper leeward side shown in FIGS. 6 and 7 is formed on the other end side of the upper leeward tank 82 (the side where the ejector outlet side space 23c is formed). Furthermore, as shown in FIG. 7, the other end side space 82d on the upper leeward side communicates with the ejector outlet side space 23c via the leeward side communication hole 82e.

  As described above, the leeward evaporator 18 is formed with the second outflow side heat exchanging portion 18a for evaporating the outflow refrigerant flowing out of the diffuser portion 15d. Accordingly, the other leeward side space 82d on the upper leeward side constitutes a distribution space to which the leeward side tube 81 constituting the second outflow side heat exchanging portion 18a is connected.

  Furthermore, in this embodiment, the number of the leeward side tubes 81 connected to the other end side space 82d on the upper leeward side is set to about a quarter (25%) of the total number NL of the leeward side tubes 81. . Accordingly, the heat exchange area occupied by the second outflow side heat exchange part 18a in the total heat exchange area of the leeward evaporator 18 when viewed from the flow direction of the blown air is about a quarter (25%). It becomes.

Further, when the passage sectional area of one leeward side tube 81 is ATb, the passage sectional area (second passage sectional area) AT2 of the refrigerant flow path in the second outflow side heat exchange section 18a is expressed by the following formula F2. Can be represented.
AT2 = 0.25 × NL × ATb (F2)
That is, the second passage cross-sectional area AT2 can be determined by the number of leeward side tubes 81 connected to the other end side space 82d on the upper leeward side.

  The tube side space 82b and the counter tube side space 82c shown in FIG. 5 are sandwiched between one end side space 82a on the upper leeward side and the other end side space 82d on the upper leeward side from both longitudinal ends of the upper leeward tank 82. Has been placed.

  The tube side space 82b is a space including a space formed on the side close to the leeward side tube 81 among the spaces partitioned by the partition member 821, and the anti-tube side space 82c is a space partitioned by the partition member 821. Among these, it is a space including a space formed on the side far from the leeward side tube 81.

  As shown in FIG. 5, the non-tube side space 82c communicates with the ejector suction side space 23b via the suction side communication hole 82f. Thereby, the non-tube side space 82c communicates with the refrigerant suction port 15c of the ejector 15 via the ejector suction side space 23b.

  Further, as shown in FIG. 2, first and second lower leeward separators 831 and 832 that extend perpendicularly to the longitudinal direction of the lower leeward tank 83 and partition the internal space are arranged inside the lower leeward tank 83. Has been. Thus, the internal space of the lower leeward tank 83 is divided into three spaces: a lower leeward side one end side space 83a, a lower leeward side intermediate side space 83b, and a lower leeward side other end side space 83c.

  The lower leeward side one end side space 83 a is formed on one end side of the lower leeward side tank 83. The other end side space 83 c on the lower leeward side is formed on the other end side of the lower leeward side tank 83. The intermediate space 83b on the lower leeward side is disposed so as to be sandwiched between one end side space 83a on the lower leeward side and the other end side space 83c on the lower leeward side from both longitudinal ends of the lower leeward tank 83. Furthermore, the other end side space 83c on the lower leeward side communicates with the internal space of the lower leeward tank via the lower communication hole 83d as shown in FIG.

  Further, as shown in FIGS. 2 and 3, an upper leeward separator 721 that extends perpendicularly to the longitudinal direction of the upper windward tank 72 is disposed inside the upper windward tank 72. Thereby, the internal space of the upper windward tank 72 is partitioned into two spaces, that is, an upper windward one end side space 72a and an upper windward upper end side space 72b.

  The upper windward one end side space 72 a shown in FIGS. 4 and 5 is formed on one end side of the upper windward tank 72 and communicates with the refrigerant outlet 24 b provided in the joint portion 24. That is, the one end side space 72a on the upper windward side forms a collective space to which the windward side tube 71 constituting the third outflow side heat exchanging portion 17b is connected.

  Furthermore, in this embodiment, the number of the windward side tubes 71 connected to the one end side space 72a on the upper windward side is about 2/3 (67%) of the total number of the windward side tubes 71. Therefore, when viewed from the flow direction of the blown air, of the total heat exchange area of the windward evaporator 17, the area occupied by the third outflow side heat exchange part 17b is about two thirds (67%). .

Further, since the dimensional specifications of the windward side tube 71 are the same as those of the leeward side tube 81, the passage cross-sectional area (third passage cross-sectional area) AT3 in the refrigerant flow path of the third outflow side heat exchanging portion 17b is expressed by the following formula F3. Can be represented.
AT3 = 0.67 × NL × ATb (F3)
That is, the third passage cross-sectional area AT3 can be determined by the number of the windward tubes 71 connected to the one end side space 72a on the upper windward side.

  6 and 7 is formed on the other end side of the upper windward tank 72 and communicates with the ejector outlet side space 23c. Furthermore, as shown in FIGS. 6 and 7, the upper windward other end side space 72b communicates with the ejector outlet side space 23c via the windward side communication hole 72c.

  As described above, the windward evaporator 17 is formed with the first outflow side heat exchange unit 17a for evaporating the outflow refrigerant flowing out of the diffuser unit 15d. Therefore, the upper windward other end side space 72b constitutes a distribution space to which the windward tube 71 constituting the first outflow side heat exchange section 17a is connected.

  Furthermore, in this embodiment, about 2/3 (67%) of the windward side tube 71 is connected to the one end side space 72a on the upper windward side, and therefore connected to the other end side space 72b on the upper windward side. The number of windward tubes 71 to be used is about the remaining third (33%). Therefore, when viewed from the flow direction of the blown air, the area occupied by the first outflow side heat exchange section 17a is about one third (33%) of the total heat exchange area of the upwind evaporator 17. .

In addition, the passage cross-sectional area (first passage cross-sectional area) AT1 of the refrigerant flow path in the first outflow side heat exchanging portion 17a can be expressed by the following formula F4.
AT1 = 0.33 × NL × ATb (F4)
That is, the first passage cross-sectional area AT1 is determined by the number of the windward side tubes 71 connected to the other end side space 72b on the upper windward side.

  Furthermore, in this embodiment, the total number of the windward side tubes 71 in the windward side evaporator 17 and the total number of the leeward side tubes 81 in the leeward side evaporator 18 are the same number. Therefore, when viewed from the flow direction of the blown air, the heat exchange area of the first outflow side heat exchange section 17a (33% of the total heat exchange area of the windward evaporator 17) is the second outflow side heat exchange section 18a. It is larger than the heat exchange area (25% of the total heat exchange area of the leeward evaporator 18).

  Therefore, as shown in FIGS. 2 and 3, in this embodiment, the passage cross-sectional area of the windward side communication hole 72c is set larger than the passage cross-sectional area of the leeward side communication hole 82e. More specifically, the windward side communication hole 72c is formed by four communication holes, and the leeward side communication hole 82e is formed by two communication holes, so that the total passage cross-sectional area of the windward side communication hole 72c is reduced. The total passage cross-sectional area of the hole 82e is set larger.

  Next, the joint part 24 will be described. The joint portion 24 is a connecting member provided with a refrigerant inlet 24 a connected to the outlet side of the temperature type expansion valve 13 and a refrigerant outlet 24 b connected to the inlet side of the compressor 11. The joint portion 24 is formed of the same material as the constituent members of the evaporators 17 and 18, and is brazed and joined to one side of the storage tank 23, the upper leeward tank 72, and the upper leeward tank 82. .

  Further, as shown in the exploded perspective view of FIG. 8, the joint portion 24 includes a block member 241 in which a refrigerant inlet 24a and a refrigerant outlet 24b are formed, and a plurality of plate members (in the present embodiment, the first member To fourth plate members 242, 243, 244 and 245).

  The first to fourth plate members 242 to 245 are formed with a refrigerant passage that guides the refrigerant flowing from the refrigerant inlet 24a to the ejector inlet side space 23a side when the plate members 242 to 245 are stacked. First to fourth inflow passage holes 242a, 243a, 244a, 245a are formed.

  Furthermore, when the plate members 242 to 245 are stacked on the first to fourth plate members 242 to 245, the refrigerant flowing out from the one end side space 72a on the upper windward side of the upper windward tank 72 is transferred to the refrigerant outlet 24b. First to fourth outflow passage holes 242b, 243b, 244b and 245b are formed to form a refrigerant passage leading to

  Of the plurality of plate members 242 to 24, the second inflow passage hole 243a of the second plate 243 disposed from the block member 241 toward the storage tank 23 side is shown in the enlarged plan view of FIG. Thus, the arc-shaped hole 243c and the circular hole 243d are formed. The most downstream portion of the arc-shaped hole 243c in the refrigerant flow is formed in a shape extending in the tangential direction of the outer peripheral portion of the circular hole 243d.

  As a result, the refrigerant that has flowed into the second inflow passage hole 243a of the second plate 243 through the first inflow passage hole 242a of the first plate 242 enters the arc-shaped hole 243c as shown by the solid line arrow in FIG. And flows into the circular hole 243d. Further, the refrigerant flowing into the circular hole 243d flows into the third and fourth inflow passage holes 244a and 245a of the third and fourth plates 244 and 245 while turning along the outer peripheral side wall surface of the circular hole 243d. To do.

  The refrigerant that has flowed into the third and fourth inflow passage holes 244a and 245a of the third and fourth plates 244 and 245 is swirling centered by the centrifugal force of the swirling flow, like the centrifugal gas-liquid separation means. The gas phase refrigerant is unevenly distributed on the side, and the liquid phase refrigerant is unevenly distributed on the outer peripheral side. Then, the refrigerant in the two-phase separation state flows into the ejector inlet side space 23 a of the storage tank 23.

  Next, the refrigerant flow path formed in the evaporator unit 20 integrated as described above will be described with reference to the explanatory view of FIG. The refrigerant flowing in from the refrigerant inlet 24a of the joint portion 24 flows into the ejector inlet side space 23a of the storage tank 23, as indicated by an arrow R1 in FIG.

  As indicated by an arrow R12, the refrigerant flowing into the ejector inlet side space 23a passes through a refrigerant flow flowing into the nozzle portion 15a of the ejector 15 and a communication path functioning as a fixed throttle 19, as indicated by an arrow R2. The refrigerant flow is branched into the refrigerant flow flowing into the one end side space 82a of the upper leeward tank 82.

  At this time, in the present embodiment, since the refrigerant flowing into the ejector inlet side space 23a is swirling, the liquid phase refrigerant unevenly distributed on the outer peripheral side of the ejector inlet side space 23a is preferentially discharged to the fixed throttle 19 side, The remaining gas-liquid two-phase refrigerant can flow into the nozzle portion 15a of the ejector 15.

  That is, the upstream branching portion 14 of the present embodiment is formed in the ejector inlet side space 23a. Further, in the present embodiment, the refrigerant passage formed by the second to fourth inflow passage holes 243a, 244a, 245a of the joint portion 24 swirls into the refrigerant in the ejector inlet side space 23a that forms the upstream branching portion 14. A swirling flow generating means for generating a flow is configured.

  The refrigerant that has flowed into the nozzle portion 15a of the ejector 15 joins the suction refrigerant sucked from the refrigerant suction port 15c, and flows out from the diffuser portion 15d. The refrigerant that has flowed out of the diffuser portion 15d flows into the ejector outlet side space 23c of the storage tank 23 as indicated by an arrow R3.

  The refrigerant that has flowed into the ejector outlet side space 23c flows through the windward side communication hole 72c through the refrigerant flow (broken arrow R4) flowing into the other end side space 72b of the upper windward side tank 72, and through the leeward side communication hole 82e. Thus, the refrigerant is diverted into the refrigerant flow (arrow R6) flowing into the other end side space 82d of the upper leeward tank 82. Therefore, the downstream branching portion 16 of the present embodiment is formed inside the ejector outlet side space 23c.

  The refrigerant that has flowed into the other end side space 72b of the upper upwind tank 72, as indicated by the broken line arrow R5, is connected to the other end side space 72b of the upper upwind tank 72, that is, the first outflow tube 71 group. The windward side tube 71 group which comprises the side heat exchange part 17a passes through from the upper side to the lower side, and flows into the lower windward side tank 73.

  On the other hand, the refrigerant flowing into the other end side space 82d of the upper leeward side tank 82 is, as shown by the arrow R7, the leeward side tube 81 group connected to the other end side space 82d of the upper leeward side tank 82, that is, the second The leeward side tube 81 group constituting the outflow side heat exchanging portion 18 a passes from the upper side to the lower side and flows into the other end side space 83 c of the lower leeward side tank 83.

  Further, the refrigerant that has flowed into the other end side space 83c of the lower leeward tank 83 flows into the lower leeward tank 73 through a communication path (not shown) as indicated by a broken arrow R8.

  That is, in this embodiment, when it sees from the flow direction of blowing air, it arrange | positions so that at least one part of the 1st outflow side heat exchange part 17a and the 2nd outflow side heat exchange part 18a may superpose | polymerize. In addition, the first outflow side heat exchanging portion 17a and the second outflow side heat exchanging portion 18a are connected to the flow of the outflow refrigerant flowing out of the diffuser portion 15d by the refrigerant inlet sides and the refrigerant outlet sides communicating with each other. They are connected in parallel.

  The refrigerant that flows out from the first outflow side heat exchange unit 17a and flows into the lower windward tank 73 and the refrigerant that flows out from the second outflow side heat exchange unit 18a and flows into the lower upside tank 73 are the lower upwind tank 73. And flows into the windward side tube 71 group constituting the third outflow side heat exchanging portion 17b.

  The refrigerant flowing into the windward side tube 71 group constituting the third outflow side heat exchanging part 17b moves the windward side tube 71 group constituting the third outflow side heat exchanging part 17b from the lower side as indicated by the broken arrow R9. It passes upward and flows into the one end side space 72 a of the upper windward tank 72. The refrigerant that has flowed into the one end side space 72a of the upper windward tank 72 flows out from the refrigerant outlet 24b of the joint portion 24, as indicated by a dashed arrow R10.

  At this time, in this embodiment, the superheat degree of the refrigerant on the outlet side of the evaporator unit 20 is adjusted so as to approach the reference superheat degree by acting on the temperature type expansion valve 13, so that the outlet side of the third outflow side heat exchange part 17b is adjusted. The refrigerant becomes a gas phase refrigerant having a superheat degree. Accordingly, as shown by the hatched area in FIG. 10, an upwind superheat region SH <b> 1 in which a superheated gas-phase refrigerant flows is formed in the windward evaporator 17.

  Further, the refrigerant that has flowed from the ejector inlet side space 23a into the one end side space 82a of the upper leeward tank 82 flows into the leeward side tube 81 group constituting the suction side heat exchanging portion 18b, and the arrow R13 → arrow R14 → arrow. It flows while changing direction three times in the order of R15 → arrow R16. And as shown by arrow R17, it guide | induces to the refrigerant | coolant suction port 15c side of the ejector 15 through the anti-tube side space 82c.

  More specifically, the refrigerant that has flowed into the one end side space 82 a of the upper leeward side tank 82 flows into the one end side space 82 a of the upper leeward side tank 82 → the one end side space 83 a of the lower leeward side tank 83 → the upper leeward side tank 82. It flows in the order of the tube side space 82b → the intermediate side space 83b of the lower leeward side tank 83 → the non-tube side space 82c of the upper leeward side tank 82 → the ejector suction side space 23b of the storage tank 23.

  At this time, in the present embodiment, the refrigerant on the refrigerant outlet side of the suction side heat exchange unit 18b is a gas phase refrigerant having a superheat degree. Accordingly, the leeward evaporator 18 is formed with a leeward superheat region SH2 through which a superheated gas-phase refrigerant flows, as indicated by hatching in FIG. Further, the windward-side superheat degree region SH1 and the leeward-side superheat degree region SH2 are shifted from each other so as not to overlap when viewed from the flow direction of the blown air.

  Next, the electric control unit of the ejector refrigeration cycle 10 of the present embodiment will be described. An air conditioning control device (not shown) is composed of a well-known microcomputer including a CPU, ROM, RAM, etc. and its peripheral circuits, and performs various calculations and processing based on a control program stored in the ROM, and is connected to the output side. The operations of the various controlled devices 11, 12c, 20a and the like are controlled.

  In addition, the air conditioning control device includes an inside air temperature sensor that detects the vehicle interior temperature, an outside air temperature sensor that detects the outside air temperature, a solar radiation sensor that detects the amount of solar radiation in the vehicle interior, and the temperature of the air blown from the evaporator unit 20 ( Sensor groups such as an evaporator temperature sensor for detecting the evaporator temperature) are connected, and the detection values of these air conditioning sensor groups are input.

  Further, an operation panel (not shown) is connected to the input side of the air conditioning control device, and operation signals from various operation switches provided on the operation panel are input to the air conditioning control device. As various operation switches provided on the operation panel, an air conditioning operation switch that requests air conditioning, a vehicle interior temperature setting switch that sets the vehicle interior temperature, and the like are provided.

  Note that the air conditioning control device of this embodiment is configured such that control means for controlling the operation of various control target devices connected to the output side is integrally configured. The configuration (hardware and software) for controlling the operation of the device constitutes the control means of each control target device. For example, in this embodiment, the structure which controls the action | operation of the compressor 11 comprises the discharge capability control means.

  Next, the operation of the ejector refrigeration cycle 10 of the present embodiment having the above configuration will be described. When the air conditioning operation switch on the operation panel is turned on (ON), the air conditioning control device operates the compressor 11, the cooling fan 12c, the blower fan 20a, and the like.

  Thereby, the compressor 11 sucks the refrigerant, compresses it, and discharges it. The high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12. The refrigerant flowing into the radiator 12 is condensed by exchanging heat with the outside air blown from the cooling fan 12c in the condensing unit 12a. The refrigerant cooled by the condensing unit 12a is gas-liquid separated by the receiver unit 12b.

  The liquid phase refrigerant separated by the receiver unit 12b flows into the temperature type expansion valve 13 and is depressurized. At this time, the valve opening degree of the temperature type expansion valve 13 is adjusted so that the superheat degree of the refrigerant on the outlet side of the evaporator unit 20 approaches the reference superheat degree. The refrigerant decompressed by the temperature type expansion valve 13 flows into the refrigerant inlet 24 a of the evaporator unit 20.

  The flow of the refrigerant flowing into the evaporator unit 20 is branched at the upstream branching portion 14 formed in the ejector inlet side space 23a of the storage tank 23. One of the branched refrigerant flows into the nozzle portion 15a of the ejector 15 and is isentropically decompressed and injected. The refrigerant flowing out of the suction side heat exchange unit 18b of the leeward evaporator 18 is sucked from the refrigerant suction port 15c of the ejector 15 by the suction action of the jet refrigerant.

  The injection refrigerant injected from the nozzle portion 15a and the suction refrigerant sucked from the refrigerant suction port 15c flow into the diffuser portion 15d of the ejector 15. In the diffuser portion 15d, the velocity energy of the refrigerant is converted into pressure energy by expanding the refrigerant passage area. Thereby, the pressure of the mixed refrigerant of the injection refrigerant and the suction refrigerant increases.

  The flow of the refrigerant that has flowed out of the diffuser portion 19d is branched by the downstream branching portion 16 formed in the ejector outlet side space 23c of the storage tank 23. The refrigerant flow branched off at the downstream branching section 16 is divided into the first outflow side heat exchange section 17a of the upwind evaporator 17 and the second outflow side heat exchange section of the leeward evaporator 18 connected in parallel with each other. It flows into 18a.

  More specifically, one of the refrigerants branched at the downstream branching portion 16 flows into the first outflow side heat exchange portion 17a of the windward evaporator 17. The refrigerant that has flowed into the first outflow side heat exchanger 17a absorbs heat from the blown air blown by the blower fan 20a and evaporates. Thereby, the blowing air blown by the blower fan 20a is cooled.

  The other refrigerant branched at the downstream branching section 16 flows into the second outflow side heat exchange section 17b of the leeward evaporator 18. The refrigerant that has flowed into the second outflow side heat exchange unit 17b absorbs heat from the blown air after passing through the first outflow side heat exchange unit 17a and evaporates. As a result, the blown air after passing through the first outflow side heat exchange section 17a is further cooled.

  The refrigerant that has flowed out of the first outflow side heat exchange unit 17a and the second outflow side heat exchange unit 18a joins and flows into the third outflow side heat exchange unit 17b of the windward evaporator 17. The refrigerant flowing into the third outflow side heat exchanging portion 17b absorbs heat from the blown air blown by the blower fan 20a and evaporates. Thereby, the blowing air blown by the blower fan 20a is cooled.

  The refrigerant that has flowed out from the third outflow side heat exchanging portion 17b flows out from the refrigerant outlet 24b of the evaporator unit 20. The refrigerant flowing out from the refrigerant outlet 24b of the evaporator unit 20 is sucked into the compressor 11 and compressed again.

  On the other hand, the other refrigerant branched at the upstream branching section 14 flows into the fixed throttle 19 and is decompressed in an isenthalpy manner, and flows into the suction side heat exchange section 18 b of the leeward evaporator 18. The refrigerant that has flowed into the suction side heat exchange unit 18b evaporates by absorbing heat from the blown air that has passed through the first outflow side heat exchange unit 17a or the third outflow side heat exchange unit 17b. As a result, the blown air after passing through the first outflow side heat exchange unit 17a or the third outflow side heat exchange unit 17b is further cooled.

  The refrigerant that has flowed out of the suction side heat exchange unit 18b is sucked from the refrigerant suction port 15c of the ejector 15 as described above.

  As described above, according to the ejector refrigeration cycle 10 of the present embodiment, the air blown into the passenger compartment can be cooled by the evaporator unit 20.

  Further, in the evaporator unit 20 of the present embodiment, the refrigerant on the downstream side of the third outflow side heat exchanging portion 17b is caused to flow out from the refrigerant outlet 24b, so that the refrigerant is pressurized in the compressor 11 by the diffuser portion 15d of the ejector 15 Can be inhaled. Therefore, according to the ejector type refrigeration cycle 10 of the present embodiment, the power consumption of the compressor 11 is reduced and the cycle is reduced as compared with a normal refrigeration cycle apparatus in which the refrigerant evaporation pressure in the evaporator and the pressure of the suction refrigerant are equal. The improvement of the coefficient of performance (COP) can be aimed at.

  Further, in the evaporator unit 20 of the present embodiment, the refrigerant evaporation pressure in the first to third outflow side heat exchanging parts 17a, 18a, 17b is set to the refrigerant pressure increased by the diffuser part 15d, and the refrigerant suction port of the ejector 15 is used. The refrigerant evaporation pressure in the suction side heat exchange unit 18b connected to 15c can be set to a low refrigerant pressure immediately after being reduced in pressure by the nozzle unit 15a.

  Accordingly, when viewed from the wind flow direction, the region where the first outflow side heat exchanging portion 17a and the suction side heat exchanging portion 18b overlap, or the third outflow side heat exchanging portion 17b and the suction side heat exchanging portion 18b overlap. In the area to be used, the temperature difference between the refrigerant evaporation temperature and the blown air in each heat exchanging portion can be secured, and the blown air can be efficiently cooled.

  Here, in the ejector 15 of the present embodiment, as described in the above-described formula F1, the refrigerant flow rate (suction flow rate) of the suction refrigerant that flows out of the suction side heat exchange unit 18b and is sucked from the refrigerant suction port of the ejector 15. ) The refrigerant flow rate (outflow flow rate) G of the outflow refrigerant flowing out of the diffuser portion 15d of the ejector 15 is larger than that of Ge.

  For this reason, in the evaporator unit 20, the pressure loss which arises when an outflow refrigerant | coolant distribute | circulates tends to become large. Further, if the pressure loss generated when the refrigerant flowing out increases, the pressure of the refrigerant sucked into the compressor is lowered. Therefore, the COP improvement effect obtained by configuring the above-described ejector refrigeration cycle. Will not be able to get enough.

  On the other hand, according to the evaporator unit 20 of the present embodiment, the second outflow side heat exchange provided in the first outflow side heat exchange section 17a provided in the upwind evaporator 17 and the downwind evaporator 18 is provided. The part 18a is connected in parallel to the flow of the effluent refrigerant, and the effluent refrigerant can flow into both the first outflow side heat exchange part 17a and the second outflow side heat exchange part 18a.

  Therefore, the passage cross-sectional area of the refrigerant passage through which the outflow refrigerant flows can be increased as compared with the case where the outflow refrigerant flows through either the first outflow side heat exchange unit 17a or the second outflow side heat exchange unit 18a. it can. As a result, it is possible to reduce the pressure loss that occurs when the outflow refrigerant having a larger flow rate than the suction refrigerant flows through the evaporator unit 20.

  Furthermore, in the evaporator unit 20 of the present embodiment, the first outflow side heat exchange unit 17a and the second outflow side heat exchange unit 18a are superposed at least partially when viewed from the flow direction of the blown air. It arrange | positions and the refrigerant | coolant inlet sides and refrigerant | coolant outlet sides of the 1st outflow side heat exchange part 17a and the 2nd outflow side heat exchange part 18a are connecting.

  Therefore, the 1st outflow side heat exchange part 17a and the 2nd outflow side heat exchange part 18a can be arranged near, and the refrigerant which guides the outflow refrigerant to the 1st outflow side heat exchange part 17a and the 2nd outflow side heat exchange part 18a The pressure loss of the flow path can be reduced. Therefore, the pressure loss that occurs when the refrigerant flows through the evaporator unit 20 can be more effectively reduced.

  Further, in the evaporator unit 20 of the present embodiment, a so-called tank and tube type heat exchanger structure is adopted as the windward evaporator 17 and the leeward evaporator 18, and the first outflow is caused by a part of the windward tube 71. The side heat exchange part 17a is comprised, and the 2nd outflow side heat exchange part 18a is comprised by a part of the leeward side tube 81. FIG.

  Therefore, it is possible to easily realize a configuration in which the refrigerant flow path of the first outflow side heat exchange unit 17a and the refrigerant flow path of the second outflow side heat exchange unit 18a are connected in parallel to the flow of the outflow refrigerant. it can.

  Further, according to the study by the present inventors, the ejector refrigeration cycle 10 provided with the evaporator unit 20 of the present embodiment is different from the ejector refrigeration cycle provided with the conventional evaporator unit. It has been confirmed that the cooling performance of the blown air can be improved.

  This will be described in more detail using the graphs of FIGS. The ratio of the leeward side heat exchange section on the horizontal axis in FIGS. 11 to 13 is the ratio of the second outflow side heat exchange section 18a in the leeward evaporator 18. Therefore, the leeward side heat exchange part ratio may be expressed as the leeward side outflow side heat exchange part ratio.

  More specifically, the leeward side heat exchange part ratio is an area ratio AL2 / ALA of the second heat exchange part area AL2 to the total heat exchange part area ALA. The total heat exchange part area ALA is the total area of the heat exchange part of the leeward evaporator 18 when viewed from the flow direction of the blown air. Moreover, 2nd heat exchange part area AL2 is an area of the 2nd outflow side heat exchange part 18a when it sees from the flow direction of blowing air.

  In the evaporator unit that uses the total heat exchange region of the leeward evaporator 18 as a suction side heat exchange unit that evaporates the suction refrigerant sucked from the refrigerant suction port 15c of the ejector 15 as in the prior art, the second The outflow side heat exchange part 18a is not provided. Therefore, in the evaporator unit that uses the total heat exchange area of the leeward evaporator 18 as the suction side heat exchange section, the area ratio AL2 / ALA is zero.

  Further, the degree of improvement in the cooling performance on the vertical axis of FIG. 11 is determined in advance in a state where the operation of the compressor 11 is controlled so that the refrigerant pressure at the refrigerant outlet 24b of the evaporator unit 20 becomes a predetermined reference pressure. The average temperature drop degree of the blown air when the blower air of the reference air volume is cooled by the evaporator unit 20 is adopted.

  In the evaporator unit 20, as the area ratio AL2 / ALA is increased, it is possible to reduce the pressure loss that occurs when the outflow refrigerant flows through the evaporator unit 20. Therefore, as the area ratio AL2 / ALA is increased, the flow rate of the refrigerant flowing into the windward evaporator 15 is easily increased, and the cooling performance of the windward evaporator 15 can be improved as shown in FIG. it can. Furthermore, the power consumption of the compressor 11 can be reduced by this effect.

  On the other hand, as the area ratio AL2 / ALA is increased, in the leeward side evaporator 18, the proportion of the second outflow side heat exchange section 18a having a higher refrigerant evaporation temperature than the suction side heat exchange section 18b increases. . Therefore, as shown in FIG. 13, as the area ratio AL2 / ALA is increased, the cooling performance of the leeward evaporator 18 decreases.

  Therefore, in this embodiment, by using the above-described degree of improvement in cooling performance, the effect of reducing the pressure loss due to the provision of the second outflow side heat exchange unit 18a in the leeward evaporator 18 and the leeward evaporator 18 The influence of the cooling performance deterioration by having provided the 2nd outflow side heat exchange part 18a is evaluated comprehensively.

As a result, as shown in FIG. 11, when the flow rate ratio Ge / G described in the above formula F1 is 0.7, the area ratio AL2 / ALA is set so as to satisfy the following formula F5. Thus, it was confirmed that the degree of improvement in cooling performance was increased.
0 <AL2 / ALA ≦ 0.6 (F5)
In other words, within the range that satisfies Formula F5, the second outflow side heat exchange unit 18a is provided in the leeward evaporator 18 rather than the influence of the cooling performance deterioration due to the provision of the second outflow side heat exchange unit 18a. It has been found that the effect of reducing the pressure loss due to is increased.

  Furthermore, it was confirmed that the degree of improvement in cooling performance increases as the flow rate ratio Ge / G decreases. This is because the flow rate of the injected refrigerant can be increased by increasing the nozzle portion side flow rate Gnoz flowing into the nozzle portion 15a as the flow rate ratio Ge / G is reduced. Thereby, the pressure | voltage rise amount of the refrigerant | coolant in the diffuser part 15d can be increased, and the refrigerant | coolant evaporation temperature in the suction side heat exchange part 18b can be reduced.

  That is, in the ejector refrigeration cycle 10 of the present embodiment, in addition to the effect of reducing the pressure loss by adopting the evaporator unit 20, the flow rate ratio Ge / G is reduced, so that the ejector refrigeration cycle 10 as a whole is reduced. The cooling performance of the blown air can be effectively improved. And the COP improvement effect by comprising an ejector type refrigerating cycle can fully be acquired.

  Therefore, in the present embodiment, it is expressed that the ejector refrigeration cycle 10 having the following features is also described for the purpose of sufficiently obtaining the COP improvement effect by configuring the ejector refrigeration cycle. Can do.

That is, a compressor (11) that compresses and discharges the refrigerant;
A radiator (12) for radiating the refrigerant discharged from the compressor (11);
An upstream branch (14) that branches the flow of the refrigerant flowing out of the radiator (12);
The refrigerant is sucked by the nozzle part (15a) for depressurizing one of the refrigerants branched at the upstream branch part (14) and the suction action of the high-speed jet refrigerant jetted from the nozzle part (15a). Ejector (15b) having a refrigerant suction port (15c) and a body portion (15b) formed with a pressure increasing unit (15d) for mixing and increasing the pressure of the jetted refrigerant and the suctioned refrigerant sucked from the refrigerant suction port (15c) )When,
A downstream branching section (16) for branching the flow of the refrigerant flowing out from the pressure increasing section (15),
An upwind evaporator (17) disposed on the upwind side of the flow of air blown into the space to be cooled;
A leeward evaporator (18) disposed on the leeward side of the air flow with respect to the windward evaporator (17);
Pressure reducing means (19) for reducing the pressure of one of the refrigerants branched at the upstream branching section (14),
The upwind evaporator (17) is provided with a first outflow side heat exchanging part (17a) for exchanging heat from the one outflow refrigerant flowing out of the downstream branch part (16) with the air. And
The leeward evaporator 18 includes a second outflow side heat exchanging portion (18a) that exchanges heat with the air to evaporate the other outflow refrigerant flowing out of the downstream branch portion (16), and the decompression means ( 19) a suction-side heat exchange section (18b) is provided for allowing the refrigerant decompressed in 19) to exchange heat with the air to evaporate and to flow out to the refrigerant suction port (15c) side;
The ejector-type refrigeration cycle, wherein the first outflow side heat exchange section (17a) and the second outflow side heat exchange section (18a) are connected in parallel to the flow of the outflow refrigerant. Can also be described as being explained.

Further, in the ejector refrigeration cycle having the above characteristics, when the flow rate of the effluent refrigerant is an effluent flow rate G and the flow rate of the suction refrigerant is a suction flow rate Ge,
Ge / G ≦ 0.7
It may be. More preferably, Ge / G ≦ 0.5 may be satisfied, or Ge / G may be configured to approach 0.3.

  As described above, in the ejector refrigeration cycle 10 of the present embodiment, the cooling performance of the blown air can be improved.

  By the way, as described above, the refrigerant evaporation temperature in the second outflow side heat exchange unit 18a of the leeward evaporator 18 is higher than the refrigerant evaporation temperature in the suction side heat exchange unit 18b. For this reason, there exists a possibility that temperature distribution may arise in the ventilation air cooled with the evaporator unit 20. FIG.

On the other hand, according to the study by the present inventors, the user feels uncomfortable with the temperature difference ΔT obtained by subtracting the minimum temperature from the maximum temperature of the blown air cooled by the evaporator unit 20, as shown in FIG. In order to obtain a temperature difference (for example, 5 ° C. or less) that does not allow the user to remember, the area ratio AL2 / ALA may be set so as to satisfy Formula F6 below.
0 <AL2 / ALA ≦ 0.25 (F6)
Further preferably, the area ratio AL2 / ALA may be set so as to satisfy Formula F7.
0.15 ≦ AL2 / ALA ≦ 0.25 (F7)
According to this, while being able to suppress the temperature difference ΔT, it is possible to aim at the maximum value for the cooling performance improvement degree described in FIG.

  Furthermore, in the evaporator unit 20 of this embodiment, since the windward side evaporator 17 and the leeward side evaporator 18 are comprised with the tank and tube type heat exchanger, it is the 2nd outflow side heat exchange part 18a, for example. By changing the number of leeward side tubes 81 constituting the heat exchange area AL2 and the area ratio AL2 / ALA of the second outflow side heat exchange section 18a can be easily changed.

  The same applies to the heat exchange area AU1 of the first outflow side heat exchange unit 17a and the heat exchange area AU3 of the third outflow side heat exchange unit 17b.

  Furthermore, in the evaporator unit 20 of the present embodiment, the windward superheat region SH1 and the leeward superheat region SH2 are arranged so as to be shifted from each other when viewed from the flow direction of the blown air. Thereby, it can suppress further that temperature distribution will arise in the ventilation air cooled in the evaporator unit 20. FIG.

  That is, even the blown air that has not sufficiently cooled after passing through the windward superheat region SH1 of the windward evaporator 17 is sufficiently absorbed by the leeward evaporator 18 due to the amount of latent heat of evaporation of the refrigerant being absorbed. Can be cooled to. On the other hand, the blown air passing through the leeward superheat degree region SH2 of the leeward evaporator 18 is sufficiently cooled by the heatward evaporator 17 absorbing the heat amount of the latent heat of vaporization of the refrigerant. As a result, it is possible to further suppress the occurrence of temperature distribution in the blown air cooled by the evaporator unit 20.

  By the way, in an evaporator applied to a vapor compression refrigeration cycle apparatus, generally, the dryness of the refrigerant increases from the refrigerant inlet side toward the refrigerant outlet side, and the refrigerant density decreases. For this reason, if the refrigerant passage area on the refrigerant inlet side and the refrigerant passage area on the refrigerant outlet side are set to be equal, the pressure loss that occurs when the refrigerant flows through the refrigerant outlet side tends to increase. In order to suppress such an increase in pressure loss, it is desirable that the refrigerant passage area on the refrigerant outlet side is larger than the refrigerant passage area on the refrigerant inlet side.

Therefore, in the present embodiment, as described in the mathematical expressions F2 to F4, the first to third passage cross-sectional areas AT1, AT2, AT3 of the refrigerant flow paths in the first to third outflow side heat exchange units 17a, 18a, 17b. Is determined so as to satisfy the relationship of the following formula F8.
AT3 ≧ AT1 + AT2 (F8)
That is, the first passage cross-sectional area AT1 of the first outflow-side heat exchange portion 17a that allows the refrigerant flowing out from the diffuser portion 15d to pass through the third passage cross-sectional area AT3 of the third outflow-side heat exchange portion 17b in parallel. It is set to be larger than the total value of the second outflow side heat exchange section 18a and the second passage sectional area AT2.

  This suppresses an increase in pressure loss that occurs when the refrigerant flows through the third outflow side heat exchange unit 18b closer to the refrigerant outlet side than the first outflow side heat exchange unit 17a and the second outflow side heat exchange unit 18a. be able to.

  Furthermore, in the evaporator unit 20 of this embodiment, since the windward side evaporator 17 and the leeward side evaporator 18 are comprised with the tank and tube type heat exchanger, it is the 1st outflow side heat exchange part 17a, for example. The first passage cross-sectional area AT1 of the first outflow side heat exchanging portion 17a can be easily changed by changing the number of the leeward side tubes 71 constituting the.

  The same applies to the second passage cross-sectional area AT2 of the second outflow side heat exchanging portion 18a and the third passage cross-sectional area AT3 of the third outflow side heat exchanging portion 17b.

  Further, in the evaporator unit 20 of the present embodiment, the partition member 821 is arranged inside the upper leeward tank 82, and as described with reference to FIG. An anti-tube side space 82c is formed. According to this, since a space partitioned in the vertical direction can be formed in the upper leeward tank 82, various refrigerant flow paths can be formed in the evaporator unit 20.

  Further, in the evaporator unit 20 of the present embodiment, the joint portion 24 in which the refrigerant inlet 24 a and the refrigerant outlet 24 are formed is connected to the side surface on one end side of the storage tank 23, the upper windward tank 72, and the upper leeward tank 82. Is arranged. According to this, when forming the ejector-type refrigeration cycle 10, the evaporator unit 20 and other components (for example, the temperature type expansion valve 13) can be easily connected.

  In the present embodiment, the swirling flow generating means for generating a swirling flow in the refrigerant in the upstream branching portion 14 by the refrigerant passage formed by the second to fourth inflow passage holes 243a, 244a, 245a of the joint portion 24 is provided. It is composed. Accordingly, the gas-liquid two-phase refrigerant can flow into the nozzle portion 15 a of the ejector 15, and the liquid-phase refrigerant can flow into the fixed throttle 19.

  According to this, boiling of the refrigerant | coolant in the nozzle part 15a can be accelerated | stimulated, and the energy conversion efficiency (nozzle efficiency) at the time of converting the pressure energy of a refrigerant | coolant into kinetic energy in the nozzle part 15a can be improved. Furthermore, the enthalpy of the refrigerant flowing into the suction side heat exchange unit 18b can be reduced, and the refrigerating capacity exhibited by the suction side heat exchange unit 18b can be increased.

(Second Embodiment)
In the present embodiment, as shown in FIG. 15, the refrigerant flow in the suction-side heat exchange unit 18b is changed by changing the shape of the partition member arranged in the upper leeward tank 82, as shown in FIG. An example in which the path is changed will be described. FIG. 15 is a drawing corresponding to FIG. 10 of the first embodiment. Further, in FIG. 15, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals. The same applies to the following drawings.

  More specifically, the partition member 823 of the present embodiment is configured by a partition plate extending in the longitudinal direction of the upper leeward tank 82 and two partition plates extending vertically in the longitudinal direction. As a result, as shown in FIG. 15, the internal space of the upper leeward side tank 82 of the present embodiment is divided into three spaces: a tube side space 82b, an anti-tube side space 82c, and an upper leeward side other end side space 82d. It is partitioned.

  Furthermore, in the present embodiment, the first lower leeward separator 831 described in the first embodiment is abolished. As a result, as shown in FIG. 15, the internal space of the lower leeward side tank 83 of the present embodiment is partitioned into two spaces, one end side space 83a on the lower leeward side and the other end side space 83c on the lower leeward side. ing. Other configurations are the same as those of the first embodiment.

  Therefore, in the evaporator unit 20 of the present embodiment, the other refrigerant branched at the upstream branching portion 14 is passed through the fixed throttle 19 and the tube side space 82b of the upper leeward tank 82 as shown by the arrow R12. Flow into.

  The refrigerant that has flowed into the tube-side space 82b of the upper leeward tank 82 flows into the leeward tube 81 group constituting the suction-side heat exchange unit 18b, and flows while changing the direction once in the order of arrow R13 → arrow R16. And as shown by arrow Ra17, it guide | induces to the refrigerant | coolant suction port 15c side of the ejector 15 via the anti-tube side space 82c.

  More specifically, the refrigerant flowing into the tube side space 82b of the upper leeward tank 82 is converted into the tube side space 82b → the one end side space 83a of the lower leeward side tank 83 → the anti-tube side space 82c of the upper leeward side tank 82 → It flows in the order of the ejector suction side space 23b of the storage tank 23. The flow of the refrigerant in the other evaporator units 20 is the same as that in the first embodiment.

  Therefore, even if the ejector refrigeration cycle 10 including the evaporator unit 20 of the present embodiment is operated, the same effect as that of the first embodiment can be obtained. That is, the pressure loss that occurs when the refrigerant flows through the evaporator unit 20 can be reduced. Further, in the ejector refrigeration cycle including the evaporator unit, a COP improvement effect can be sufficiently obtained.

  Further, in the evaporator unit 20 of the present embodiment, the passage cross-sectional area of the refrigerant flow path in the suction side evaporation unit 18b is enlarged by reducing the number of refrigerant direction changes in the suction side evaporation unit 18b as compared with the first embodiment. it can. Therefore, it is possible to reduce the pressure loss that occurs when the refrigerant flows through the suction side evaporator 18b.

(Third embodiment)
In the present embodiment, an example will be described in which the refrigerant flow path in the suction-side heat exchange unit 18b is changed by adopting a capillary tube 19a as a fixed throttle as shown in FIG. 16 with respect to the first embodiment. .

  More specifically, in this embodiment, the capillary tube 19a is brazed and joined to the side surface of one end side of the evaporator unit 20 (the side to which the joint portion 24 is joined). For this reason, in this embodiment, the communication path which connects the ejector inlet side space 23a and the one end side space 82a on the upper leeward side described in FIG. 4 of the first embodiment is eliminated. Further, the upstream branching portion 14 is disposed inside the joint portion 24 or upstream of the refrigerant inlet 24 a of the joint portion 24.

  Further, as the partition member 824 arranged in the upper leeward tank 82, a partition member extending in the longitudinal direction of the upper leeward tank 82 and two partition plates extending vertically in the longitudinal direction is adopted. Yes. For this reason, as shown in FIG. 16, the internal space of the upper leeward tank 82 of the present embodiment is divided into three spaces: a tube side space 82b, an anti-tube side space 82c, and an upper leeward side other end side space 82d. It is partitioned. Other configurations are the same as those of the first embodiment.

  Accordingly, in the evaporator unit 20 of the present embodiment, the other refrigerant branched at the upstream branching portion 14 passes through the capillary tube 19a as indicated by an arrow R121. Then, the refrigerant is decompressed when passing through the capillary tube 19 a and flows into the one end side space 83 a of the lower leeward tank 83.

  The refrigerant that has flowed into the one end side space 83a of the lower leeward side tank 83 flows into the leeward side tube 81 group constituting the suction side heat exchanging portion 18b, and is turned twice in the order of arrow R14 → arrow R15 → arrow R16. While flowing. And as shown by arrow R17, it guide | induces to the refrigerant | coolant suction port 15c side of the ejector 15 through the anti-tube side space 82c.

  More specifically, the refrigerant that has flowed into the one end side space 83 a of the lower leeward side tank 83 flows into the one end side space 83 a of the lower leeward side tank 83 → the tube side space 82 b of the upper leeward side tank 82 → the lower leeward side tank 83. It flows in the order of the intermediate side space 83 b → the anti-tube side space 82 c of the upper leeward side tank 82. The flow of the refrigerant in the other evaporator units 20 is the same as that in the first embodiment.

  Therefore, even if the ejector refrigeration cycle 10 including the evaporator unit 20 of the present embodiment is operated, the same effect as that of the first embodiment can be obtained. That is, the pressure loss that occurs when the refrigerant flows through the evaporator unit 20 can be reduced. Further, in the ejector refrigeration cycle including the evaporator unit, a COP improvement effect can be sufficiently obtained.

  Further, in the evaporator unit 20 of the present embodiment, since the number of redirections of the refrigerant in the suction side evaporator 18b is reduced compared to the first embodiment, the refrigerant is sucked on the suction side as in the second embodiment. It is possible to reduce the pressure loss that occurs when circulating through the evaporator 18b. Further, similarly to the first embodiment, when viewed from the flow direction of the blown air, it is possible to realize an arrangement in which the windward superheat region SH1 and the leeward superheat region SH2 are shifted from each other.

(Fourth to sixth embodiments)
In the first to third embodiments, the evaporator unit 20 in which the storage tank 23 is arranged in the valley between the upper windward tank 72 and the upper leeward tank 82 has been described, but in the fourth to sixth embodiments, the storage tank 23 is disposed. An example in which the arrangement of the storage tank 23 is changed without changing the basic configuration of the evaporator unit 20 will be described with respect to the first to third embodiments.

  Specifically, in the evaporator unit 20 of the fourth to sixth embodiments, as shown in FIGS. 17 to 19, the storage tank 23 is disposed above the upper leeward tank 82. Then, the height dimension (vertical dimension) of the upper windward tank 72 and the total height dimension of the storage tank 23 and the upper windward tank 82 are made to coincide with each other.

  Therefore, in the evaporator unit 20 of the fourth to sixth embodiments, the storage tank 23 does not protrude upward from the valley portion, and the application to the evaporator unit 20 (vehicle in this embodiment) is not performed. Mountability can be improved.

  More specifically, in the evaporator unit 20 of the fourth embodiment, since the refrigerant flows as shown in FIG. 17, the same effect as that of the first embodiment can be obtained. Moreover, in the evaporator unit 20 of 5th Embodiment, since a refrigerant | coolant flows as shown in FIG. 18, the effect similar to 2nd Embodiment can be acquired. Furthermore, in the evaporator unit 20 of the sixth embodiment, since the refrigerant flows as shown in FIG. 19, the same effect as that of the third embodiment can be obtained.

(Seventh embodiment)
In the present embodiment, as shown in FIG. 20, an example will be described in which the storage tank 23 is abolished and the ejector 15 is stored in the upper leeward tank 82 compared to the first embodiment.

  In the evaporator unit 20 of the present embodiment, an ejector inlet side space 23 a is formed on the upstream side of the nozzle portion 15 a inside the ejector 15. Further, the ejector 15 is disposed so as to penetrate the partition plate 821 that extends perpendicularly to the longitudinal direction of the upper leeward tank 82 and the upper leeward separator 822 in the partition member 821.

  As a result, as shown in FIG. 20, the internal space of the upper leeward tank 82 has an upper leeward side one end side space 82a, a tube side space 82b, an anti-tube side space 82c, and an upper leeward side other end side space 82d. It is divided into four spaces. The one end side space 82a on the upper leeward side is disposed on the outer peripheral side of the upstream side of the nozzle portion 15a of the ejector 15 (that is, the portion where the ejector inlet side space 23a is formed inside).

  The refrigerant suction port 15c of the ejector 15 opens in the non-tube side space 82c. The refrigerant outlet of the diffuser portion 15d of the ejector 15 opens in the other end side space 82d. Further, the downstream branching portion 16 is formed in the other end side space 82d. Other configurations are the same as those of the first embodiment.

  For this reason, in the evaporator unit 20 of the present embodiment, the refrigerant flowing in from the refrigerant inlet 24a of the joint portion 24 is formed on the upstream side of the nozzle portion 15a of the ejector 15 as indicated by an arrow R1 in FIG. It flows into the ejector inlet side space 23a.

  The refrigerant flowing into the ejector inlet side space 23a flows through the refrigerant flow flowing into the nozzle portion 15a of the ejector 15 and the communication passage functioning as the fixed throttle 19 provided on the outer peripheral wall surface of the ejector 15 as shown by an arrow R2. Thus, as shown by an arrow R12, the refrigerant flow is divided into the refrigerant flow flowing into the one end side space 82a of the upper leeward tank 82.

  Further, the refrigerant that has flowed out of the diffuser portion 15d of the ejector 15 flows into the other end side space 82d of the upper leeward tank 82, as indicated by an arrow R3. The refrigerant flowing into the other end side space 82d flows into the other end side space 72b of the upper windward tank 72 (broken line arrow R4), and the leeward side tube 81 group constituting the second outflow side heat exchanging portion 18a. To the refrigerant flow (arrow R7).

  The flow of the refrigerant in the other evaporator units 20 is the same as that in the first embodiment. That is, in the evaporator unit 20 of the present embodiment, the refrigerant flows substantially as in the first embodiment. Therefore, even if the ejector refrigeration cycle 10 including the evaporator unit 20 of the present embodiment is operated, the same effect as that of the first embodiment can be obtained.

(Eighth embodiment)
In the present embodiment, as shown in FIG. 21, an example will be described in which the storage tank 23 is abolished and the ejector 15 is stored in the upper leeward tank 82 with respect to the second embodiment.

  In the evaporator unit 20 of the present embodiment, an ejector inlet side space 23a is formed on the upstream side of the nozzle portion 15a inside the ejector 15 as in the seventh embodiment. Further, the ejector 15 is disposed so as to penetrate the partition plate 823 extending perpendicularly to the longitudinal direction of the upper leeward tank 82 and the upper leeward separator 822 in the partition member 823.

  Accordingly, as shown in FIG. 21, the internal space of the upper leeward tank 82 is partitioned into three spaces, a tube side space 82b, an anti-tube side space 82c, and an upper leeward side other end side space 82d. In this embodiment, the space on the outer peripheral side of the ejector inlet side space 23a upstream of the nozzle portion 15a of the ejector 15 also forms the tube side space 82b. Other configurations are the same as those of the second embodiment.

  For this reason, in the evaporator unit 20 of the present embodiment, the refrigerant flowing from the refrigerant inlet 24a of the joint portion 24 is formed on the upstream side of the nozzle portion 15a of the ejector 15 as indicated by an arrow R1 in FIG. It flows into the ejector inlet side space 23a.

  The refrigerant flowing into the ejector inlet side space 23a flows through the refrigerant flow flowing into the nozzle portion 15a of the ejector 15 and the communication passage functioning as the fixed throttle 19 provided on the outer peripheral wall surface of the ejector 15 as shown by an arrow R2. Thus, as shown by an arrow R12, the refrigerant is diverted into the refrigerant flow flowing into the tube side space 82b. Further, the refrigerant flowing out from the diffuser portion 15d of the ejector 15 is the same as that in the seventh embodiment.

  The refrigerant flow in the other evaporator units 20 is the same as that in the second embodiment. That is, in the evaporator unit 20 of the present embodiment, the refrigerant flows substantially as in the second embodiment. Therefore, even if the ejector refrigeration cycle 10 including the evaporator unit 20 of the present embodiment is operated, the same effect as that of the second embodiment can be obtained.

(Ninth embodiment)
In the present embodiment, as shown in FIG. 22, an example in which the storage tank 23 is eliminated and the ejector 15 is stored in the upper leeward tank 82 in the third embodiment will be described.

  In the evaporator unit 20 of the present embodiment, an ejector inlet side space 23a is formed on the upstream side of the nozzle portion 15a inside the ejector 15 as in the seventh embodiment. Further, the ejector 15 is disposed so as to penetrate the partition plate 823 extending perpendicularly to the longitudinal direction of the upper leeward tank 82 and the upper leeward separator 822 in the partition member 823.

  Thereby, as shown in FIG. 22, the internal space of the upper leeward side tank 82 is partitioned into three spaces: a tube side space 82b, an anti-tube side space 82c, and an upper leeward side other end side space 82d. In this embodiment, since the capillary tube 19a is employed as the fixed throttle, the communication path on the outer peripheral wall surface of the ejector 15 is also eliminated. Other configurations are the same as those of the third embodiment.

  For this reason, in the evaporator unit 20 of this embodiment, one refrigerant | coolant branched in the upstream branch part 14 flows into the nozzle part 15a of the ejector 15, as shown by arrow R2 of FIG. The refrigerant passes through the capillary tube 19a as indicated by an arrow R121 in FIG. Further, the refrigerant flowing out from the diffuser portion 15d of the ejector 15 is the same as that in the seventh embodiment.

  The flow of the refrigerant in the other evaporator units 20 is the same as that in the third embodiment. That is, in the evaporator unit 20 of the present embodiment, the refrigerant flows substantially as in the third embodiment. Therefore, even if the ejector refrigeration cycle 10 including the evaporator unit 20 of the present embodiment is operated, the same effect as that of the third embodiment can be obtained.

(10th Embodiment)
In the present embodiment, as shown in FIG. 23, an example in which the partition member 824 is eliminated from the ninth embodiment will be described. Therefore, in this embodiment, as shown in FIG. 23, the internal space of the upper leeward tank 82 is divided into two spaces, one end space 82a on the upper leeward side and the other end side space 82d on the upper leeward side. Yes. Further, the refrigerant suction port 15c of the ejector 15 opens in the one end side space 82a on the upper leeward side. Other configurations are the same as those of the ninth embodiment.

  For this reason, in the evaporator unit 20 of this embodiment, one refrigerant | coolant branched in the upstream branch part 14 flows into the nozzle part 15a of the ejector 15 similarly to 9th Embodiment, and the other refrigerant | coolant is Pass through the capillary tube 19a. Then, the refrigerant is decompressed when passing through the capillary tube 19 a and flows into the one end side space 83 a of the lower leeward tank 83.

  The refrigerant flowing into the one end side space 83a of the lower leeward side tank 83 flows into the leeward side tube 81 group constituting the suction side heat exchanging portion 18b, and as shown by an arrow R14, is one end side of the upper leeward side tank 82. It is guided to the refrigerant suction port 15c side of the ejector 15 through the space 82a. The flow of the refrigerant in the other evaporator units 20 is the same as that in the ninth embodiment.

  Therefore, even if the ejector-type refrigeration cycle 10 including the evaporator unit 20 of the present embodiment is operated, the pressure loss generated when the refrigerant flows through the evaporator unit 20 as in the ninth embodiment is reduced. Can do. Further, in the ejector refrigeration cycle including the evaporator unit, a COP improvement effect can be sufficiently obtained.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows without departing from the spirit of the present invention.

  In the above-described embodiment, the evaporator unit 20 in which the upstream branching section 14, the ejector 15, the downstream branching section 16, the windward evaporator 17, the leeward evaporator 18, and the fixed throttle 19 are integrated has been described. The evaporator unit 20 according to the present invention is not limited to this. At least the ejector 15, the windward evaporator 17, and the leeward evaporator 18 may be integrated. Further, in addition to the above-described components, the temperature type expansion valve 13 may be integrated.

  In the above-described embodiment, the example in which the respective component devices are integrated by brazing and joining has been described. However, various means such as screwing, caulking, welding, and adhesion can be used as an integration unit for each component device. It may be adopted. Furthermore, the COP improvement effect by comprising an ejector type refrigerating cycle can also be acquired by connecting similarly to the evaporator unit 20, without integrating each component apparatus.

  Each component apparatus which comprises the above-mentioned ejector type refrigeration cycle 10 is not limited to what was disclosed by the above-mentioned embodiment.

  For example, in the above-described embodiment, an example in which an electric compressor is employed as the compressor 11 has been described. However, the compressor 11 is driven by a rotational driving force transmitted from a vehicle traveling engine via a pulley, a belt, or the like. An engine driven compressor may be employed. Furthermore, as an engine-driven compressor, the variable capacity compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity, or the refrigerant discharge capacity can be adjusted by changing the operating rate of the compressor by intermittently connecting the electromagnetic clutch A fixed-capacity compressor can be employed.

  In the above-described embodiment, an example in which a receiver-integrated condenser is employed as the radiator 12 has been described. Further, the radiator 12 has a supercooling unit that supercools the liquid-phase refrigerant flowing out from the receiver unit 12b. A so-called subcool condenser may be employed. In addition, a radiator 12 including only the condensing unit 12a, and a receiver (receiver) that separates the gas-liquid refrigerant flowing out of the radiator 12 and flows the separated liquid-phase refrigerant downstream. It may be adopted.

  In the above-described embodiment, an example in which the ejector 15 has a fixed nozzle portion that does not change the refrigerant passage area has been described. Of course, a variable ejector having a variable nozzle portion that can change the refrigerant passage area is used. It may be used. As a specific example of the variable nozzle part, for example, a needle may be inserted into the passage of the variable nozzle part, and the position of this needle may be controlled by an electric actuator to adjust the passage area.

  In each of the above-described embodiments, the example in which the evaporator unit 20 according to the present invention is applied to the ejector refrigeration cycle 10 mounted on a vehicle has been described. However, the application of the evaporator unit 20 is not limited thereto. The present invention may be applied not only to a vehicle but also to an ejector type refrigeration cycle for stationary use.

15 Ejector 15a Nozzle part 15b Body part 15c Refrigerant suction port 15d Diffuser part (pressure increase part)
17 Windward side evaporator 17a 1st outflow side heat exchange part 18 Downwind side evaporator 18a 2nd outflow side heat exchange part

Claims (12)

A nozzle part (15a) for depressurizing the refrigerant, a refrigerant suction port (15c) for sucking the refrigerant by a suction action of the high-speed jet refrigerant jetted from the nozzle part (15a), and the jetted refrigerant and the refrigerant suction An ejector (15) having a body part (15b) in which a pressure increasing part (15d) for mixing and increasing the pressure of the suction refrigerant sucked from the mouth (15c) is formed;
An upwind evaporator (17) disposed on the upwind side of the flow of air blown into the space to be cooled;
A leeward evaporator (18) disposed on the leeward side of the air flow with respect to the windward evaporator (17),
The upwind evaporator (17) is provided with a first outflow side heat exchange section (17a) that exchanges heat with the air to evaporate the outflow refrigerant flowing out of the pressure increasing section (15d),
In the downwind evaporator (18), the refrigerant drawn out to the second outflow side heat exchange section (18a) for exchanging heat with the air to evaporate the outflow refrigerant and the refrigerant suction port (15c) A suction side heat exchange section (18b) for exchanging heat with air and evaporating is provided;
The evaporator unit, wherein the first outflow side heat exchange section (17a) and the second outflow side heat exchange section (18a) are connected in parallel to the flow of the outflow refrigerant. When viewed from the air flow direction, the first outflow side heat exchange section (17a) and the second outflow side heat exchange section (18a) are arranged so that at least a part thereof is polymerized,
The first outflow side heat exchanging portion (17a) and the second outflow side heat exchanging portion (18a) are communicated with each other at the refrigerant inlet sides and with each other at the refrigerant outlet sides. The evaporator unit according to claim 1, wherein the evaporator unit is connected in parallel to the flow of the outflow refrigerant. When viewed from the air flow direction, the total area of the heat exchange section that exchanges heat between the refrigerant and the air in the leeward evaporator (18) is defined as a total heat exchange section area ALA, and the second outflow side heat. When the area of the exchange part is the second heat exchange part area AL2,
0 <AL2 / ALA ≦ 0.6
The evaporator unit according to claim 1 or 2, wherein When viewed from the air flow direction, the total area of the heat exchange section that exchanges heat between the refrigerant and the air in the leeward evaporator (18) is defined as a total heat exchange section area ALA, and the second outflow side heat. When the area of the exchange part is the second heat exchange part area AL2,
0 <AL2 / ALA ≦ 0.25
The evaporator unit according to claim 1 or 2, wherein When viewed from the air flow direction, the total area of the heat exchange section that exchanges heat between the refrigerant and the air in the leeward evaporator (18) is defined as a total heat exchange section area ALA, and the second outflow side heat. When the area of the exchange part is the second heat exchange part area AL2,
0.15 ≦ AL2 / ALA ≦ 0.25
The evaporator unit according to claim 1 or 2, wherein The windward evaporator (17) includes a plurality of windward tubes (71) through which a refrigerant flows and a windward tank (72, 73) that collects or distributes the refrigerant flowing through the plurality of windward tubes (71). )
The windward tanks (72, 73) are formed in a shape extending in the stacking direction of the plurality of windward tubes (71),
The leeward evaporator (18) includes a plurality of leeward tubes (81) through which a refrigerant flows and a leeward tank (82, 83) that collects or distributes the refrigerant flowing through the plurality of leeward tubes (81). )
The leeward tank (82, 83) is formed in a shape extending in a direction parallel to the leeward tank (72, 73) in the stacking direction of the plurality of leeward tubes (81),
Further, the upwind evaporator (17) is a refrigerant in which the refrigerant flowing out from the first outflow side heat exchange section (17a) and the refrigerant flowing out from the second outflow side heat exchange section (18a) are merged. The evaporator unit according to any one of claims 1 to 5, further comprising a third outflow side heat exchanging portion (17b) for exchanging heat with the air for evaporation. A storage tank (23) that forms an ejector outlet side space (23c) through which the refrigerant that has flowed out of the pressure increasing section (15d) flows;
The ejector outlet side space (23c) is a space (72b) to which the windward side tube (71) constituting the first outflow side heat exchange part (17a) of the windward side tanks (72, 73) is connected. To the space (82d) to which the leeward side tube (81) constituting the second outflow side heat exchange part (18a) of the leeward side tank (82, 83) is connected. The evaporator unit according to claim 6, wherein the evaporator unit is provided. The passage cross-sectional area of the refrigerant flow path in the first outflow side heat exchange section (17a) is defined as a first passage cross-sectional area AT1, and the passage cross-sectional area of the refrigerant flow path in the second outflow side heat exchange section (18a) is a second. When the passage sectional area AT2 and the passage sectional area of the refrigerant flow path in the third outflow side heat exchange section (18b) is the third passage sectional area AT3,
AT3 ≧ AT1 + AT2
The evaporator unit according to claim 6 or 7, wherein A partition member (821) that extends in the longitudinal direction of the leeward tank (82) and partitions the internal space of the leeward tank (82) is disposed inside the leeward tank (82),
The partition member (821) includes a tube side space (82b) including a space formed inside the leeward side tank (82) on a side close to the leeward side tube (81), and the tube side space (82b). ) To the non-tube side space (82c) including the space formed on the side farther from the leeward side tube (81) than
The evaporator unit according to any one of claims 6 to 8, wherein the anti-tube side space (82c) communicates with the refrigerant suction port (15c).   The refrigerant inlet (24a) for allowing refrigerant to flow into the upstream side of the nozzle part (15a) and the refrigerant outlet (24b) for flowing out refrigerant on the downstream side of the third outlet side heat exchange part (17b) The evaporator unit according to any one of claims 6 to 9, wherein the evaporator unit is disposed on one end side in the longitudinal direction of the leeward tank (82, 83) and the leeward tank (82, 83). An upstream branching section (14) for branching the flow of the refrigerant flowing in from the outside, and causing one of the branched refrigerants to flow out toward the nozzle section (15a);
Pressure reducing means (19, 19a) for reducing the pressure of the other refrigerant branched at the upstream branching portion (14),
The swirl flow generating means (24, 243a ... 245a) for generating a swirl flow in the refrigerant in the upstream branch (14) is further provided. Evaporator unit.   When viewed from the air flow direction, an upwind superheat region (SH1) through which a superheated gas-phase refrigerant flows in the upwind evaporator (17) and the downwind evaporator (18). 12. The evaporator unit according to claim 1, wherein the leeward superheat degree region (SH <b> 2) through which the gas-phase refrigerant having a superheat degree flows is arranged so as to be shifted from each other.

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