JP2011185504A - Evaporator unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To suppress temperature distribution of an evaporator unit including a sensible heat exchange part carrying out heat exchange between a gaseous refrigerant and air sent to a cooling object space. <P>SOLUTION: In the evaporator unit 20, the sensible heat exchange part 20e and an outflow side evaporation part 20c are provided in an upwind side heat exchanger 23 disposed in an air flow upwind side, and a suction side evaporation part 20d and an outflow side evaporation part 20c are provided in a downwind side heat exchanger 24. When seen from a flowing direction of air, the sensible heat exchange part 20e and the suction side evaporation part 20d are mutually overlapped, and the outflow side evaporation parts 20c are disposed so as to mutually overlap. By this, of air cooled by each evaporation part and heat exchange part 20c, 20d, 20e, air cooled in the sensible heat exchange part 20e becoming the highest temperature can be cooled further in the suction side evaporation part 20d becoming the lowest temperature, and as the entire evaporator unit 20, the temperature distribution of the air sent to the cooling object space can be suppressed. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

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

  2. Description of the Related Art Conventionally, an ejector refrigeration cycle including an ejector as refrigerant decompression means is known. Since this type of ejector has a refrigerant suction port in addition to the refrigerant inlet / outlet, the ejector type refrigeration cycle has an ejector and other cycles compared to a normal refrigeration cycle having a decompression means having only a refrigerant inlet / outlet. Connection with component equipment tends to be complicated.

  For this reason, in an ejector-type refrigeration cycle, the mountability when mounted on a product such as an air conditioner is likely to deteriorate with respect to a normal refrigeration cycle. On the other hand, for example, Patent Document 1 discloses an apparatus in which an ejector and an evaporator are integrated as an evaporator unit. Such integration is effective as a means for improving the mountability of the ejector refrigeration cycle in the product.

  Specifically, in the evaporator unit of Patent Document 1, an ejector, an outflow side evaporation unit that evaporates the refrigerant that flows out from the diffuser unit of the ejector, and a gas-liquid separator that separates the gas and liquid of the refrigerant that flows out from the outflow side evaporation unit A suction-side evaporation unit that evaporates the liquid-phase refrigerant flowing out from the gas-liquid separator and flows out to the refrigerant suction port side of the ejector, and a gas-phase refrigerant flowing out from the gas-liquid separator to circulate The sensible heat exchange part that flows out into the unit is integrated.

  Furthermore, in the evaporator unit of Patent Document 1, the sensible heat exchange unit, the outflow side evaporation unit, and the suction side evaporation unit are arranged in a flat plate shape, and a heat medium such as water or glycol is transferred to the sensible heat exchange unit → outflow side evaporation unit. → Cooled by passing in the order of the suction side evaporation section (in order of decreasing heat exchange temperature). The cooled heat medium is allowed to flow into a heat medium-air heat exchanger called a heater and heat exchange between the heat medium and air is performed so that the heat medium can absorb heat from the air.

International Publication No. 2009/090073 Pamphlet

  However, in the configuration in which the air is cooled via a heat medium and the air is blown to the space to be cooled as in the evaporator unit of Patent Document 1, the mountability when the above-described ejector refrigeration cycle is mounted on a product. Even if the improvement effect can be obtained, the air conditioner as a whole needs to be provided with a heat medium circulation circuit for circulating the heat medium and a heat medium-air heat exchanger. As a result, the configuration of the entire air conditioner becomes complicated.

  In order to avoid complication of the configuration of the air conditioner (product) as a whole, the refrigerant is directly exchanged with the refrigerant by directly exchanging heat between the refrigerant and the air blown into the space to be cooled in the evaporator unit. Means for absorbing heat are conceivable. However, as in the evaporator unit of Patent Document 1, when the sensible heat exchange unit, the outflow side evaporation unit, and the suction side evaporation unit are arranged in a flat plate shape and the air is directly cooled, the temperature of the air blown out from the evaporator unit is increased. Distribution will occur.

  In particular, since the sensible heat exchange part can only absorb the sensible heat from the air, the air blown from the sensible heat exchange part of the evaporator unit can be refrigerated like the outflow side evaporation part or the suction side evaporation part. However, the temperature rises with respect to the air blown out from the heat exchanging section that can absorb the heat of evaporation latent heat from the air.

  An object of this invention is to suppress the temperature distribution of the evaporator unit containing the sensible heat exchange part which heat-exchanges a gaseous-phase refrigerant | coolant and the air ventilated to cooling object space in view of the said point.

In order to achieve the above object, in the first aspect of the present invention, the refrigerant is sucked from the refrigerant suction port (21c) by the flow of the high-speed jet refrigerant jetted from the nozzle portion (21a) for depressurizing the refrigerant, and the refrigerant An ejector (21) for mixing and suctioning the suction refrigerant sucked from the suction port (21c) and increasing the pressure; a gas-liquid separator (22) for separating the gas-liquid of the refrigerant flowing out from the ejector (21); The windward heat exchanger (23) disposed on the windward side of the airflow that is exchanged with the refrigerant and blown into the space to be cooled, and the airflow leeward with respect to the windward heat exchanger (23) A leeward heat exchanger (24) disposed on the side,
The leeward heat exchanger (23) is provided with a sensible heat exchanger (20e) for exchanging heat between the gas-phase refrigerant flowing out of the gas-liquid separator (22) and the air, and the leeward heat exchanger (24). Is provided with a suction-side evaporation section (20d) for evaporating the liquid-phase refrigerant flowing out from the gas-liquid separator (22) by exchanging heat with air and flowing it out to the refrigerant suction port (21c) side. The exchange part (20e) and the suction side evaporation part (20d) are characterized by an evaporator unit arranged so as to overlap each other when viewed from the air flow direction.

  Here, in the sensible heat exchange section (20e), heat exchange is performed between the gas-phase refrigerant that has flowed out of the gas-liquid separator (22) and the air, so that the air only absorbs sensible heat. On the other hand, in the suction side evaporation section (20d), the liquid phase refrigerant that has flowed out of the gas-liquid separator (22) and the air are heat-exchanged, so that the air absorbs the latent heat of vaporization of the refrigerant. Therefore, the temperature of the air cooled by the suction side evaporation part (20d) becomes lower than the temperature of the air cooled by the sensible heat exchange part (20e).

  On the other hand, according to the first aspect of the present invention, the sensible heat exchange part (20e) is provided in the upwind heat exchanger (23), and the suction side evaporation part (20d) is provided in the leeward heat exchanger (24). In addition, the sensible heat exchange part (20e) and the suction side evaporation part (20d) are arranged so as to overlap each other when viewed from the air flow direction.

  Therefore, the air cooled by the sensible heat exchange part (20e) can be further cooled by the suction side evaporation part (20d). As a result, the air cooled in the sensible heat exchanger (20e) is avoided from being blown out of the evaporator unit at the same temperature, and the air blown into the space to be cooled as the entire evaporator unit. Temperature distribution can be suppressed.

In the invention according to claim 2, the refrigerant is sucked from the refrigerant suction port (21c) by the flow of the high-speed jetted refrigerant jetted from the nozzle portion (21a) for decompressing the refrigerant, and the refrigerant suction port (21c). An ejector (21) that increases the pressure by mixing the suction refrigerant sucked from the jet refrigerant and the injection refrigerant, a gas-liquid separator (22) that separates the gas-liquid of the refrigerant flowing out from the ejector (21), and exchanges heat with the refrigerant. With respect to the windward side heat exchanger (23) disposed on the windward side of the flow of air blown into the space to be cooled and the windward side heat exchanger (23), it is disposed on the leeward side of the airflow. A leeward heat exchanger (24),
The leeward heat exchanger (23) is provided with a sensible heat exchanger (20e) for exchanging heat between the gas-phase refrigerant flowing out of the gas-liquid separator (22) and the air, and the leeward heat exchanger (24). Include a suction-side evaporation section (20d) for evaporating the liquid-phase refrigerant flowing out from the gas-liquid separator (22) by heat exchange with air and flowing it out to the refrigerant suction port (21c) side, and an ejector (21 ) Is provided with an outflow side evaporation section (20c) for evaporating the refrigerant flowing out from the air by exchanging heat with air and flowing out to the inlet side of the gas-liquid separator (22), a sensible heat exchange section (20e), and suction At least one of the side evaporation section (20d) and the outflow side evaporation section (20c) is characterized by an evaporator unit disposed so as to overlap each other when viewed from the air flow direction.

  Here, as described above, the temperature of the air cooled by the suction side evaporation section (20d) and the temperature of the air cooled by the outflow side evaporation section (20c) were cooled by the sensible heat exchange section (20e). It becomes lower than the temperature of the air.

  On the other hand, according to the invention described in claim 2, the sensible heat exchanger (20e) is provided in the windward heat exchanger (23), and the suction side evaporator (20d) and the outflow side evaporator (20c). At least one of them is provided in the leeward heat exchanger (24), and when viewed from the air flow direction, the sensible heat exchange part (20e), the suction side evaporation part (20d) and the outflow side evaporation part At least one of (20c) is arranged to be polymerized with each other.

  Therefore, the air cooled by the sensible heat exchange part (20e) can be further cooled by at least one of the suction side evaporation part (20d) and the outflow side evaporation part (20c). As a result, the air cooled in the sensible heat exchanger (20e) is avoided from being blown out of the evaporator unit at the same temperature, and the air blown into the space to be cooled as the entire evaporator unit. Temperature distribution can be suppressed.

  In addition, “sensible heat exchange part (20e) and at least one of suction side evaporation part (20d) and outflow side evaporation part (20c) in this claim is superposed on each other when viewed from the air flow direction. The phrase “arranged so that the sensible heat exchange part (20e) and the suction side evaporation part (20d) are superposed on each other when viewed from the air flow direction, The heat exchange part (20e) and the outflow side evaporation part (20c) are arranged so as to be polymerized with each other, and the sensible heat exchange part (20e) and both the evaporation parts (20c, 20d) are polymerized with each other. It is meant to include being arranged in.

  Further, as in the invention according to claim 3, in the evaporator unit according to claim 2, the wind-side heat exchanger (23) is provided with a part of the outflow side evaporator (20c), The heat exchange section (20e) and the suction side evaporation section (20d) are arranged so as to overlap each other when viewed from the air flow direction, and are provided on the windward side heat exchanger (23). (20c) and the outflow side evaporator (20c) provided in the leeward heat exchanger (24) are arranged so as to overlap each other when viewed from the air flow direction.

  Here, in the ejector-type refrigeration cycle, the refrigerant evaporating pressure (refrigerant evaporating temperature) in the suction side evaporating part (20d) is changed from the refrigerant evaporating pressure (refrigerant evaporating temperature) in the outflow side evaporating part (20c) by the boosting action of the ejector (21). ) Can be raised. Therefore, the temperature of the air cooled by the suction side evaporation unit (20d) is lower than the temperature of the air cooled by the outflow side evaporation unit (20c).

  Therefore, the temperature of the air cooled in each part decreases in the order of the sensible heat exchange part (20e) → the outflow side evaporation part (20c) → the suction side evaporation part (20d). On the other hand, according to the invention described in claim 3, when viewed from the air flow direction, the sensible heat exchange section (20e) and the suction side evaporation section (20d) are polymerized with each other, and further, the outflow side Since the evaporation parts (20c) are superposed on each other, the temperature distribution of the air blown from the evaporator unit to the space to be cooled can be effectively suppressed.

  That is, the sensible heat exchange part (20e) and the suction side evaporation part (20d) are superposed on each other, so that the temperature of the air blown from the suction side evaporation part (20d) in the leeward side heat exchanger (24) and the leeward side. A temperature difference with the temperature of the air which blows off from an outflow side evaporation part (20c) among side heat exchangers (24) can be made small. As a result, the temperature distribution of the air blown from the evaporator unit to the space to be cooled can be effectively suppressed.

  According to a fourth aspect of the present invention, in the evaporator unit according to any one of the first to third aspects, at least one of the windward side heat exchanger (23) and the leeward side heat exchanger (24) is A plurality of tubes (23a, 24a) through which refrigerant that exchanges heat with air circulates and tank parts (23c, 23d, 24c, 24d) that perform the distribution and collection functions of the refrigerant to the plurality of tubes (23a, 24a). The gas-liquid separator (22) is characterized by being formed by tank parts (23c, 23d, 24c, 24d).

  According to this, the internal space of the tank parts (23c, 23d, 24c, 24d) can be used effectively, and the gas-liquid separator (22) is used as the windward side heat exchanger (23) and the leeward side heat exchanger. As compared with the case of arranging outside (24), the evaporator unit as a whole can be reduced in size.

  According to a fifth aspect of the present invention, in the evaporator unit according to the fourth aspect, the liquid phase refrigerant flowing out from the gas-liquid separator (22) is placed inside the tank portion (23c, 23d, 24c, 24d). A pressure reducing mechanism (22a) for reducing the pressure is arranged. According to this, compared with the case where the decompression mechanism (22a) is disposed outside the windward side heat exchanger (23) and the leeward side heat exchanger (24), the overall evaporator unit can be reduced in size. it can.

  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 a typical perspective view of the evaporator unit of 1st Embodiment. It is a typical longitudinal section of the lower tank part of the leeward heat exchanger of a 1st embodiment. It is a graph explaining the temperature distribution of the evaporator unit of 1st Embodiment. It is a whole block diagram of the ejector type refrigerating cycle of 2nd Embodiment. It is a typical perspective view of the evaporator unit of 2nd Embodiment. It is a graph explaining the temperature distribution of the evaporator unit of 2nd Embodiment. It is a typical perspective view of the evaporator unit of 3rd Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 4th Embodiment. It is a typical perspective view of the evaporator unit of 4th Embodiment. It is a graph explaining the temperature distribution of the evaporator unit of 4th Embodiment. It is a whole block diagram of the ejector-type refrigerating cycle of 5th Embodiment. It is a typical perspective view of the evaporator unit of 5th Embodiment. It is a graph explaining the temperature distribution of the evaporator unit of 5th Embodiment.

(First embodiment)
1-4, the evaporator unit 20 which concerns on 1st Embodiment of this invention is demonstrated. The evaporator unit 20 is applied to an ejector refrigeration cycle 10 that is a refrigeration cycle including an ejector, and may also be called an ejector refrigeration cycle evaporator unit or an ejector integrated evaporator unit.

  FIG. 1 is an overall configuration diagram of an ejector refrigeration cycle 10 to which an evaporator unit 20 of the present embodiment is applied. This ejector-type refrigeration cycle 10 is applied to a vehicle air conditioner and has a function of cooling blown air that is blown into a vehicle interior that is a space to be cooled. Further, the ejector refrigeration cycle 10 of the present embodiment employs a normal chlorofluorocarbon refrigerant as the refrigerant, and constitutes a subcritical cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant.

  First, in the ejector refrigeration cycle 10, the compressor 11 sucks and compresses the refrigerant. The compressor 11 is disposed in the engine room of the vehicle, and is driven to rotate by receiving a driving force from a vehicle travel engine (not shown). Furthermore, in this embodiment, a variable capacity compressor that can adjust the refrigerant discharge capacity by changing the discharge capacity is adopted as the compressor 11.

  The discharge capacity of the compressor 11 is controlled by a control signal output from an air conditioning control device (not shown). Of course, as the compressor, a fixed capacity type compressor that adjusts the refrigerant discharge capacity by changing the operating rate of the compressor operation by the on / off of the electromagnetic clutch may be adopted. Moreover, if an electric compressor is employ | adopted as the compressor 11, a refrigerant | coolant discharge capability can be adjusted by the rotation speed adjustment of an electric motor.

  A radiator 12 disposed in the engine room is connected to the refrigerant discharge side of the compressor 11. The radiator 12 is a heat exchanger for radiating heat to exchange heat between the high-pressure refrigerant discharged from the compressor 11 and the outside air blown by the cooling fan 12a to radiate the high-pressure refrigerant. The cooling fan 12a 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 inlet side of the high-pressure side refrigerant flow path 13 a of the internal heat exchanger 13 is connected to the outlet side of the radiator 12. The internal heat exchanger 13 exchanges heat between the refrigerant on the outlet side of the radiator 12 that passes through the high-pressure side refrigerant flow path 13a and the refrigerant on the suction side of the compressor 11 that passes through the low-pressure side refrigerant flow path 13b. The refrigerant passing through 13a is cooled.

  Thereby, the refrigerant | coolant which flows in into the outflow side evaporator 20c and the suction side evaporator 20d provided in the windward side heat exchanger 23 and the leeward side heat exchanger 24 of the evaporator unit 20 mentioned later, and these evaporators 20c, 20d The enthalpy difference with the refrigerant flowing out of the refrigerant can be increased, and the refrigeration capacity exhibited by these evaporation units 20c and 20d can be expanded.

  As a specific configuration of the internal heat exchanger 13, a configuration in which refrigerant pipes forming the high-pressure side refrigerant flow path 13a and the low-pressure side refrigerant flow path 13b are brazed and joined to exchange heat, or the high-pressure side refrigerant flow path 13a is used. It is possible to employ a double-pipe heat exchanger configuration in which the low-pressure side refrigerant flow path 13b is disposed outside the inner tube that forms the tube.

  The refrigerant inlet 20a side of the evaporator unit 20 of the present embodiment is connected to the outlet side of the high-pressure side refrigerant flow path 13a of the internal heat exchanger 13. Further, the inlet side of the low-pressure side refrigerant flow path 13 b of the internal heat exchanger 13 is connected to the refrigerant outlet 20 b side of the evaporator unit 20. The suction side of the compressor 11 is connected to the outlet side of the low-pressure side refrigerant flow path 13b.

  The evaporator unit 20 is disposed in an air passage formed in an indoor unit of a vehicle air conditioner (not shown), and blown air blown from the blower fan 14 toward the vehicle interior and a refrigerant flowing inside. Is cooled by exchanging heat. The blower fan 14 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.

  Further, the evaporator unit 20 includes an ejector 21, a gas-liquid separator 22 that separates the gas-liquid of the refrigerant that has flowed out of the ejector 21, of the cycle constituent devices that constitute the ejector refrigeration cycle 10, and exchanges heat with the refrigerant to blow air. For the upwind heat exchanger 23 arranged on the upwind side of the air flow and the upwind heat exchanger 23, one leeward side heat exchanger 24 or the like arranged on the downwind side of the flow of the blown air is provided. It is integrated as a unit.

  The detailed configuration of the evaporator unit 20 will be described with reference to FIG. 2 in addition to FIG. FIG. 2 is a schematic perspective view showing the arrangement of the constituent devices constituting the evaporator unit 20 and the internal configuration of the evaporator unit 20, and the flow of the refrigerant in the evaporator unit 20 is indicated by a thick solid line. Shown with arrows. Moreover, the up and down arrows in FIG. 2 indicate the up and down directions when the evaporator unit 20 is mounted on the vehicle, and the white arrows indicate the flow direction of the blown air.

  First, the ejector 21 functions as a refrigerant depressurizing unit that depressurizes the refrigerant flowing out from the high-pressure side refrigerant flow path 13a of the internal heat exchanger 13, and circulates the refrigerant by the suction action of the injected refrigerant that is injected at a high speed. It functions as a refrigerant circulating means.

  Specifically, the ejector 21 includes a nozzle portion 21a for reducing the refrigerant passage area of the refrigerant flowing out from the high-pressure side refrigerant passage 13a of the internal heat exchanger 13 to an isentropic pressure reduction, and an internal portion thereof. A body portion 21b that accommodates the nozzle portion 21a and forms the outer shell of the ejector 21 is provided.

  The body portion 21b is formed in a substantially cylindrical shape extending in the injection direction of the injection refrigerant injected from the nozzle portion 21a (the axial direction of the nozzle portion 21a), and on the cylindrical wall surface of the body portion 21b, the refrigerant of the nozzle portion 21a is formed. A refrigerant suction port 21c that is disposed so as to communicate with the injection port and sucks the refrigerant that has flowed out from the suction side evaporation unit 20d of the leeward heat exchanger 24 described later is formed.

  Further, in the refrigerant flow path formed in the body portion 21b, the refrigerant injected from the nozzle portion 21a and the refrigerant suction port 21c are sucked from the refrigerant flow downstream of the nozzle portion 21a and the refrigerant suction port 21c. A diffuser portion 21d is formed as a mixed pressure increasing portion that increases the pressure by mixing the suction refrigerant.

  The diffuser portion 21d is formed in a shape in which the refrigerant passage area gradually increases in the refrigerant flow direction, and increases the pressure of the mixed refrigerant by decelerating the flow rate of the mixed refrigerant of the injected refrigerant and the suction refrigerant. That is, the speed energy of the mixed refrigerant is converted into pressure energy.

  Next, the windward heat exchanger 23 exchanges heat between the blown air blown from the blower fan 14 toward the vehicle interior and the refrigerant circulating in the interior.

  More specifically, as shown in FIG. 2, the windward side heat exchanger 23 includes a plurality of tubes 23a through which the refrigerant flows, a plurality of heat exchange fins 23b that promote heat exchange between the air and the refrigerant, and This is a so-called tank-and-tube heat exchanger configured to have a pair of tank portions 23c and 23d for collecting and distributing the refrigerant with respect to each tube 23a.

  In FIG. 2, for clarity of illustration, only a part of the tubes 23a and the heat exchange fins 23b are shown, but the tubes 23a are stacked in a certain direction, and the heat exchange fins 23b are It arrange | positions between the adjacent tubes 23a. And the heat exchange core part 23e which heat-exchanges air and a refrigerant | coolant is formed of the laminated structure of this tube 23a and the heat exchange fin 23b.

  Furthermore, an upper tank part 23c and a lower tank part 23d are provided as a pair of tank parts. Both tank parts 23c and 23d are formed in the shape extended in the lamination direction of the tube 23a and the heat exchange fin 23b, and are arrange | positioned at the longitudinal direction both ends of each tube 23a.

  And the internal space of both the tank parts 23c and 23d is connected to the refrigerant path of each tube 23a. Moreover, the internal space of both tank parts 23c and 23d is partitioned into a plurality of spaces by first and second separators 23f and 23g as partition members. The spaces partitioned by the first and second separators 23f and 23g will be described later.

  The leeward side heat exchanger 24 exchanges heat between the blown air that has been blown from the blower fan 14 into the vehicle interior and passed through the upside heat exchanger 23 and the refrigerant that circulates inside. The same as the windward side heat exchanger 23.

  Therefore, the leeward heat exchanger 24 is also a tank and tube type heat exchanger having the tubes 24a, the heat exchange fins 24b, the upper tank portion 24c, and the lower tank portion 24d. The internal spaces of the upper tank portion 24c and the lower tank portion 24d of the leeward heat exchanger 24 are also partitioned into a plurality of spaces by the first and second separators 24f and 24g.

  Further, in the present embodiment, at least a part of the upper tank portions 23c, 24c of the windward side heat exchanger 23 and the leeward side heat exchanger 24, and under the windward side heat exchanger 23 and the leeward side heat exchanger 24, At least a part of the side tank portions 23d and 24d is formed of the same member, and the windward side heat exchanger 23 and the leeward side heat exchanger 24 are integrated.

  At this time, the tank parts 23c to 24d are arranged so that the longitudinal directions thereof are parallel to each other. Of course, these tank portions 23c to 24d may be formed as separate members, and may be integrally formed in the same manner by a joining means such as brazing joint, or may be similarly integrated by a mechanical fastening means such as bolt fastening. You may comprise.

  Further, in the present embodiment, the ejector 21 is disposed in the first space 241 on one end side in the longitudinal direction, which is partitioned by the first separator 24f, in the internal space of the upper tank portion 24c of the leeward heat exchanger 24, The ejector 21 and the leeward heat exchanger 24 are integrated. More specifically, the ejector 21 is disposed such that its longitudinal direction is parallel to the longitudinal direction of the upper tank portion 24 c of the leeward heat exchanger 24.

  The refrigerant inlet of the nozzle portion 21a of the ejector 21 is connected to the refrigerant inlet 20a of the evaporator unit, the refrigerant suction port 21c is opened in the first space 241, and the outlet side of the ejector 21 is further connected by the first separator 23f. It opens in the 2nd space 242 of the partitioned other longitudinal direction side. Note that the volume of the second space 242 is secured approximately twice the volume of the first space 241.

  Further, as shown in FIG. 2, the internal space of the upper tank portion 23c of the leeward heat exchanger 23 is also changed to the first separator 23f by the first separator 23f in the same manner as the upper tank portion 24c of the leeward heat exchanger 24. It is partitioned into a first space 231 and a second space 232 on the other end side. In FIG. 2, for the sake of clarity of illustration, a black circle mark is attached to the leading end of the lead line in the reference numeral indicating each space.

  Further, the second space 232 of the windward side heat exchanger 23 and the second space 242 of the leeward side heat exchanger 24 are directly communicated with each other through communication holes formed in the wall surfaces of both the upper tank portions 23c and 24c. ing. Therefore, the refrigerant that has flowed out of the ejector 21 flows into both the second space 232 of the upwind heat exchanger 23 and the second space 242 of the leeward heat exchanger 24.

  Further, as shown in FIG. 2, the upper tank portion of the leeward heat exchanger 24 is also used for the internal spaces of the lower tank portion 23d of the leeward heat exchanger 23 and the lower tank portion 24d of the leeward heat exchanger 24. Similarly to 24c, the first separators 23f and 24f respectively divide the third space 233 and 234 on one end side and the fourth space 243 and 244 on the other end side.

  The first spaces 231 and 241 of the upper tank portions 23c and 24c of the heat exchangers 23 and 24 and the third spaces 233 and 243 of the lower tank portions 23d and 24d are formed by the same group of tubes 23a and 23b. The second spaces 232, 242 of the upper tank portions 23c, 24c and the fourth spaces 234, 244 of the lower tank portions 23d, 24d are connected by the same tube 23a, 24a group.

  Further, the fourth spaces 234 and 244 of both the lower tank portions 23d and 24d are partitioned into an upper space and a lower space by second separators 23g and 24g extending in the longitudinal direction, and have a so-called two-story structure. ing. The upper spaces of the fourth spaces 234 and 244 communicate with each other through communication holes formed in the lower tank portions 23d and 24d.

  Therefore, it flows out from the tube 23a, 23b group which connects the 3rd space 234,244 of 2nd space 232,242 of lower side tank part 23d, 24d, and 2nd space 232,242 of upper side tank part 23c, 24c of both heat exchangers 23,24. The refrigerated refrigerant merges in the upper spaces of the fourth spaces 234, 244 of the lower tank portions 23d, 24d.

  The second separator 24g of the lower tank portion 24d of the leeward heat exchanger 24 is provided with a communication hole 241g that allows the upper space and the lower space to communicate with each other, and the upper space of the fourth spaces 234, 244. The refrigerant merged in step 241 flows into the lower space of the fourth space 244 of the leeward heat exchanger 24 through the communication hole 241g.

  This lower space constitutes a gas-liquid separation space that separates the gas-liquid refrigerant flowing out of the ejector 21. In other words, the gas-liquid separator 22 of the present embodiment is formed by the lower tank portion 24d of the leeward heat exchanger 24.

  Therefore, in the heat exchange core portion 23e of the windward side heat exchanger 23, the region extending from the second space 232 to the fourth space 234, and in the heat exchange core portion 24e of the leeward side heat exchanger 24, the second space. The region from 242 to the fourth space 244 functions as an outflow side evaporation section 20c that evaporates the refrigerant flowing out of the ejector 21 by exchanging heat with the blown air and evaporating it to the inlet side of the gas-liquid separator 22.

  That is, in this embodiment, a part of the outflow side evaporator 20c is provided in both the upwind heat exchanger 23 and the downwind heat exchanger 24, and the outflow side evaporation provided in the upwind heat exchanger 23 is provided. The outflow side evaporation section 20c provided in the section 20c and the leeward heat exchanger 24 is disposed so as to overlap each other when viewed from the flow direction of the blown air.

  Next, the detailed configuration of the gas-liquid separator 22 will be described with reference to FIG. FIG. 3 is a schematic longitudinal sectional view of the lower tank portion 24d of the leeward heat exchanger 24. Like FIG. 2, the refrigerant in the evaporator unit 20 (gas-liquid separator 22) is shown. The flow is indicated by thick solid arrows.

  As shown in FIG. 3, in the first separator 24f that partitions the lower tank portion 24d into the third space 243 and the fourth space 244, below the liquid level of the liquid-phase refrigerant in the gas-liquid separator 22, A liquid-phase refrigerant outlet hole 22a is formed through which the liquid-phase refrigerant separated by the gas-liquid separator 22 flows out to the third space 243 side. The liquid phase refrigerant outlet hole 22a functions as a fixed throttle (orifice) which is a pressure reducing mechanism, and depressurizes the liquid phase refrigerant flowing out from the liquid phase refrigerant outlet hole 22a.

  Here, as described with reference to FIG. 2 described above, the third space 243 of the leeward heat exchanger 24 is connected to the first space 241 of the leeward heat exchanger 24 by the tube 24a. The refrigerant suction port 21 c is open in the first space 241 of the leeward heat exchanger 24.

  Therefore, the region from the third space 243 to the first space 241 in the heat exchange core portion 24e of the leeward heat exchanger 24 causes the liquid refrigerant flowing out of the gas-liquid separator 22 to exchange heat with the blown air. It functions as a suction side evaporation section 20d that evaporates and flows out to the refrigerant suction port 21c side.

  Further, in the lower tank portion 24d, the tank wall surface forming the gas-liquid separator 22, and above the liquid surface of the liquid-phase refrigerant, the gas-phase refrigerant separated by the gas-liquid separator 22 is blown into the wind. A gas-phase refrigerant outlet hole 22 b that flows out to the lower space side of the fourth space 234 of the upper heat exchanger 23 is formed. The gas-phase refrigerant outlet hole 22b has an opening area larger than that of the liquid-phase refrigerant outlet hole 22a in order to suppress the pressure loss of the gas-phase refrigerant separated by the gas-liquid separator 22 as much as possible.

  Further, the lower space of the fourth space 234 of the windward heat exchanger 23 communicates with the third space 233 of the windward heat exchanger 23 through a communication hole formed in the first separator 23f.

  Here, as described above, the third space 233 of the windward heat exchanger 23 communicates with the first space 231 of the windward heat exchanger 23. Therefore, the region from the third space 233 to the first space 231 in the heat exchange core portion 23e of the upwind heat exchanger 23 is a region where the gas-phase refrigerant that has flowed out of the gas-liquid separator 22 exchanges heat with the blown air. It functions as the heat exchange part 20e.

  That is, in this embodiment, when the sensible heat exchange part 20e provided in the windward side heat exchanger 23 and the suction side evaporation part 20d provided in the leeward side heat exchanger 24 are viewed from the flow direction of the blown air. , Are arranged to polymerize with each other. Further, the first space 231 of the upwind heat exchanger 23 communicates with the refrigerant outlet 20 b of the evaporator unit 20.

  Next, the electric control unit of this embodiment will be described. An air conditioning control device (not shown) is composed of a well-known microcomputer including a CPU, ROM, RAM, and its peripheral circuits, and performs various calculations and processing based on an air conditioning control program stored in the ROM. The operation of various connected air conditioning control devices (for example, the compressor 11, the cooling fan 12a, the blower fan 14, etc.) is controlled.

  On the input side of the air conditioning control device, there are an inside air sensor that detects the temperature inside the vehicle, an outside air sensor that detects the outside air temperature, a solar radiation sensor that detects the amount of solar radiation in the vehicle interior, and the blown air of the blown air blown out from the evaporator unit 20 Various sensor groups for air conditioning control such as an evaporator temperature sensor for detecting temperature (evaporator temperature) are connected.

  Further, an operation panel disposed near the instrument panel in front of the passenger compartment is connected to the input side of the air conditioning control device, and operation signals are input from various air conditioning operation switches provided on the operation panel. As various air conditioning operation switches provided on the operation panel, specifically, an operation switch of a vehicle air conditioner, a vehicle interior temperature setting switch for setting the vehicle interior temperature, and the like are provided.

  Next, the operation of this embodiment in the above configuration will be described. When the operation switch of the operation panel is turned on, the air conditioning control device obtains target values such as the target refrigerant discharge capacity of the compressor 11 and the target air blowing capacity of the cooling fan 12a and the air blowing fan 14 from the detected values of the air conditioning control sensor group. The control signal is output to the compressor 11, the cooling fan 12 a, the blower fan 14, and the like so as to obtain the target value. As a result, the ejector refrigeration cycle 10 also operates.

  First, the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the radiator 12. The high-temperature and high-pressure refrigerant flowing into the radiator 12 is cooled and condensed by exchanging heat with the outdoor air blown from the cooling fan 12a. The high-pressure refrigerant flowing out of the radiator 12 flows into the high-pressure side refrigerant passage 13a of the internal heat exchanger 13, exchanges heat with the low-pressure refrigerant flowing through the low-pressure side refrigerant passage 13b, and is further cooled to lower enthalpy. Let

  The high-pressure refrigerant that has flowed out of the high-pressure side refrigerant flow path 13a of the internal heat exchanger 13 flows from the refrigerant inlet 20a of the evaporator unit 20 into the nozzle portion 21a of the ejector 21, and is decompressed in an isentropic manner. At this time, the pressure energy of the refrigerant is converted into velocity energy at the nozzle portion 21a, and the gas-liquid two-phase refrigerant is injected at a high velocity from the refrigerant injection port of the nozzle portion 21a.

  And the refrigerant | coolant in the 1st space 241 of the upper side tank part 24c of the leeward side heat exchanger 24 is attracted | sucked from the refrigerant | coolant suction opening 21c by the suction effect | action of this injection refrigerant | coolant. As described above, the refrigerant in the first space 241 is the refrigerant that has flowed out of the suction side evaporation unit 20d.

  The injection refrigerant injected from the nozzle part 21a and the suction refrigerant sucked from the refrigerant suction port 21c flow into the diffuser part 21d and are mixed. Further, in the diffuser portion 21d, the refrigerant velocity area is increased, and the velocity energy of the refrigerant is converted into pressure energy, thereby increasing the pressure of the mixed refrigerant.

  The refrigerant that has flowed out of the ejector 21 (specifically, the diffuser portion 21d) flows into the second spaces 242 and 232 of the upper tank portions 24d and 23d of the leeward heat exchanger 24 and the windward heat exchanger 23, and The air flows into the outflow side evaporator 20c provided in the leeward side heat exchanger 24 and the leeward side heat exchanger 23 from the two spaces 242, 232.

  In the outflow side evaporator 20c provided in the upwind heat exchanger 23, the refrigerant that has flowed in absorbs heat from the blown air blown from the blower fan 14 and evaporates. Moreover, in the outflow side evaporation part 20c provided in the leeward side heat exchanger 24, the refrigerant | coolant which flowed in absorbs heat from the ventilation air cooled in the outflow side evaporation part 20c provided in the upwind side heat exchanger 23. Evaporate. Thereby, the blast air after passing the outflow side evaporation part 20c of the windward heat exchanger 23 is further cooled.

  The refrigerant that has flowed out of the outflow-side evaporator 20c provided in the leeward heat exchanger 24 and the upwind heat exchanger 23 flows into the fourth space 244 and the upwind heat in the lower tank portion 24d of the leeward heat exchanger 24, respectively. It flows into the fourth space 234 of the lower tank portion 23d of the exchanger 23. And it merges through the communicating hole formed in both lower tank parts 23d and 24d.

  The merged refrigerant passes through the communication hole 241g formed in the second separator 24g of the lower tank portion 24d of the leeward heat exchanger 24, and the air formed by the lower tank portion 23d of the leeward heat exchanger 24. It flows into the liquid separator 22. In the gas-liquid separator 22, the gas-liquid of the refrigerant that has flowed in is separated.

  The gas-phase refrigerant that has flowed out of the gas-phase refrigerant outlet hole 22b of the gas-liquid separator 22 flows in the order of the lower space of the fourth space 234 of the upwind heat exchanger 23 and the third space 233 of the upwind heat exchanger 23. It flows into the sensible heat exchange part 20e provided in. In the sensible heat exchange unit 20e, the refrigerant into which the gas-phase refrigerant that has flowed in exchanges heat with the blown air blown from the blower fan 14 to cool the blown air.

  The refrigerant that has flowed out of the sensible heat exchanger 20e into the first space 231 of the windward heat exchanger 23 flows out of the refrigerant outlet 20b of the evaporator unit 20. The refrigerant flowing out from the refrigerant outlet 20b of the evaporator unit exchanges heat with the high-pressure refrigerant flowing through the high-pressure side refrigerant flow path 13a in the low-pressure side refrigerant flow path 13b of the internal heat exchanger 13, and then sucks into the compressor 11 again. And compressed.

  The liquid-phase refrigerant flowing out from the liquid-phase refrigerant outlet hole 22a of the gas-liquid separator 22 is decompressed in an enthalpy manner at the liquid-phase refrigerant outlet hole 22a and flows into the third space 233 of the leeward heat exchanger 24. Furthermore, it flows from the third space 233 into the suction side evaporation unit 20d provided in the leeward heat exchanger 24. In the suction side evaporation part 20d, the refrigerant that has flowed in passes through the sensible heat exchange part 20e provided in the windward heat exchanger 23 and absorbs heat from the cooled air to evaporate.

  Thereby, the blast air after passing the sensible heat exchange part 20e is further cooled. The refrigerant that has flowed out of the suction-side evaporation unit 20d into the first space 241 of the leeward heat exchanger 24 is sucked into the ejector 21 from the refrigerant suction port 21c of the ejector 21.

  Since the ejector type refrigeration cycle 10 of the present embodiment operates as described above, it is possible to cool the blown air blown from the blower fan 14 toward the vehicle interior by the evaporator unit 20. Furthermore, even in the evaporator unit 20 having the sensible heat exchange part 20e, the temperature distribution of the blown air blown out from the evaporator unit 20 can be suppressed.

  This will be described with reference to the temperature distribution diagram of FIG. In FIG. 4, the temperature distribution blown out as a whole of the evaporator unit 20 when the evaporator unit 20 is viewed from the leeward heat exchanger 24 side (from the direction facing the blown air flow) is indicated by a thick solid line. The temperature distribution when cooled only by the windward side heat exchanger 23 is indicated by a thick broken line, and the temperature distribution when cooled only by the leeward side heat exchanger 24 is indicated by a thick dashed line.

  Here, in the sensible heat exchange section 20e, heat exchange is performed between the gas-phase refrigerant that has flowed out of the gas-liquid separator 22 and the blown air, so that the air only absorbs sensible heat. On the other hand, in the outflow side evaporation unit 20c and the suction side evaporation unit 20d, the liquid phase refrigerant flowing out from the gas-liquid separator 22 and the blown air are subjected to heat exchange, so that the blown air absorbs the heat of the latent heat of vaporization of the refrigerant.

  Further, in the ejector-type refrigeration cycle 10, the refrigerant evaporating pressure (refrigerant evaporating temperature) in the outflow side evaporating unit 20 c is increased more than the refrigerant evaporating pressure (refrigerant evaporating temperature) in the suction side evaporating unit 20 d by the boosting action of the ejector 21. Can do.

  Therefore, as shown by the thick broken line and the thick dashed line in FIG. 4, the temperature of the air cooled by the outflow side evaporation unit 20c and the suction side evaporation unit 20d is the temperature of the air cooled by the sensible heat exchange unit 20e. Lower than. Further, the temperature of the air cooled by the suction side evaporation unit 20d is lower than the temperature of the air cooled by the outflow side evaporation unit 20c.

  On the other hand, according to this embodiment, the sensible heat exchanger 20e and the outflow side evaporator 20c are provided in the upwind heat exchanger 23, and the suction side evaporator 20d and the outflow side evaporator 20c are connected to the leeward heat exchanger. Further, when viewed from the air flow direction, the sensible heat exchange unit 20e and the suction side evaporation unit 20d are superposed on each other, and the outflow side evaporation units 20c are superposed on each other.

  Therefore, the air cooled by the sensible heat exchanger 20e having the highest temperature among the air cooled by the respective evaporators and the heat exchangers 20c, 20d, and 20e is further converted into the suction side evaporator having the lowest temperature. It can be cooled at 20d. Thereby, as shown by the thick solid line in FIG. 4, the temperature between the temperature of the blown air blown from the suction side evaporation unit 20d of the leeward heat exchanger 24 and the temperature of the blown air blown from the outflow side evaporation unit 20c. The difference can be reduced.

  As a result, the temperature distribution of the air blown into the space to be cooled can be suppressed as the entire evaporator unit 20.

  Furthermore, in this embodiment, since the gas-liquid separator 22 is formed by the lower tank portion 24d of the leeward heat exchanger 24, the internal space of the lower tank portion 24d can be used effectively. In addition, when the gas-liquid separator 22 is disposed outside the upwind heat exchanger 23 and the downwind heat exchanger 24, the pressure loss of the refrigerant flowing through the evaporator unit 20 can be suppressed, and the evaporator The overall size of the unit 20 can be reduced.

  Furthermore, in the present embodiment, the liquid-phase refrigerant outlet hole 22a that functions as a decompression mechanism is disposed in the first separator 24f in the lower tank portion 24d of the leeward heat exchanger 24. The evaporator unit 20 as a whole can be downsized as compared with the case where it is arranged outside the exchanger 23 and the leeward heat exchanger 24.

  Further, in the present embodiment, the ejector 21 connected to the refrigerant inlet 20a of the evaporator unit 20 is arranged in the first space 241 of the upper tank portion 24c of the leeward heat exchanger 24, and the refrigerant outlet 20b is exchanged with the windward heat. Since the first tank 231 communicates with the first space 231 of the upper tank portion 23c of the evaporator 23, the refrigerant inlet 20a and the refrigerant outlet 20b can be disposed close to each other, and the mountability when the evaporator unit 20 is mounted on the vehicle air conditioner. Can be improved.

(Second Embodiment)
This embodiment demonstrates the example which changed the structure of the evaporator unit 20 as shown in the whole block diagram of FIG. 5, and the typical perspective view of FIG. 6 with respect to 1st Embodiment. That is, in the first embodiment, the example in which the sensible heat exchange unit 20e and the outflow side evaporation unit 20c are provided in the windward heat exchanger 23 has been described. However, in this embodiment, the sensible heat exchange is performed in the windward heat exchanger 23. An example in which only the unit 20e is provided will be described.

  FIG. 5 is an overall configuration diagram corresponding to FIG. 1 of the first embodiment, and FIG. 6 is a schematic perspective view corresponding to FIG. 2 of the second embodiment. Further, in FIGS. 5 and 6, the same or equivalent parts as those in FIGS. The same applies to the following drawings.

  More specifically, in the evaporator unit 20 of this embodiment, as shown in FIG. 6, the 1st, 2nd separators 23f and 23g of the upwind heat exchanger 23 are abolished. Therefore, the upper tank portion 23 c of the windward heat exchanger 23 forms one internal space 230 a without being partitioned into the first and second spaces 231 and 232. Similarly, the lower tank portion 23d forms one internal space 230b without being partitioned by the third and fourth spaces 233 and 234.

  Furthermore, in this embodiment, the internal space 230a of the upper tank part 23c of the windward side heat exchanger 23 and the second space 242 of the upper tank part 24c of the leeward side heat exchanger 24 are not in direct communication. Therefore, the refrigerant that has flowed out of the diffuser portion 21 d of the ejector 21 flows only into the second space 242 of the leeward heat exchanger 24.

  Further, the gas phase refrigerant that has flowed out of the gas phase refrigerant outlet hole 22 b of the gas-liquid separator 22 flows into the internal space 230 b of the lower tank portion 23 d of the windward heat exchanger 23. The internal space 230b of the present embodiment communicates with the internal space 230a of the upper tank portion 23c via a plurality of tubes 23a.

  Therefore, in the present embodiment, the region from the second space 242 to the fourth space 244 in the heat exchange core portion 24e of the leeward heat exchanger 24 functions as the outflow side evaporation portion 20c, and the third space 243 to the second space A region reaching one space 241 functions as the suction side evaporation unit 20d. Further, the entire region from the internal space 230b to the internal space 230a in the heat exchange core portion 23e of the windward heat exchanger 23 functions as the sensible heat exchange portion 20e.

  In the present embodiment, the volume of the second space 242 of the windward heat exchanger 23 is secured about 0.5 times the volume of the first space 241, and the volume of the fourth space 244 is also the volume of the third space 243. About 0.5 times as large as The overall configuration and operation of the other evaporator units 20 and the ejector refrigeration cycle 10 are the same as those in the first embodiment.

  Therefore, when the ejector-type refrigeration cycle 10 of this embodiment is operated, even the evaporator unit 20 having the sensible heat exchanger 20e is blown out from the evaporator unit 20 as shown in the temperature distribution diagram of FIG. The temperature distribution of the blast air can be suppressed. FIG. 7 is a graph corresponding to FIG. 4 of the first embodiment.

  That is, according to the present embodiment, the sensible heat exchanger 20e is provided in the windward heat exchanger 23, the suction side evaporator 20d and the outflow side evaporator 20c are provided in the leeward heat exchanger 24, and the air flow When viewed from the direction, the sensible heat exchange part 20e and the suction side evaporation part 20d are superposed on each other, and the sensible heat exchange part 20e and the outflow side evaporation part 20c are superposed on each other.

  Therefore, the air cooled by the sensible heat exchange unit 20e having the highest temperature among the air cooled by the units 20c, 20d, and 20e is further cooled by the outflow side evaporation unit 20c and the suction side evaporation unit 20d. be able to. Thereby, as shown by the thick solid line in FIG. 6, the temperature between the temperature of the blown air blown from the suction side evaporator 20d of the leeward heat exchanger 24 and the temperature of the blown air blown from the outflow side evaporator 20c. The difference can be reduced.

  As a result, the temperature distribution of the air blown into the space to be cooled can be suppressed as the entire evaporator unit 20. Furthermore, also in the evaporator unit 20 of this embodiment, the same size reduction effect and mountability improvement effect as in the first embodiment can be obtained.

(Third embodiment)
This embodiment is a modification of the second embodiment. As shown in the schematic perspective view of FIG. 8, the evaporator unit 20 of the present embodiment is configured such that a part of the ejector 21 on the inlet side of the nozzle portion 21 a is outside the upper tank portion 24 c of the leeward heat exchanger 24. It was exposed. Other configurations and operations are the same as those of the second embodiment.

  Therefore, also in this embodiment, the temperature distribution of the blown air blown out from the evaporator unit 20 is the same as that in FIG. 7 of the second embodiment, and the same effect as in the second embodiment can be obtained. Furthermore, according to the present embodiment, the inlet side of the nozzle portion 21 a of the ejector 21 can be used as the refrigerant inlet 20 a of the evaporator unit 20.

(Fourth embodiment)
This embodiment demonstrates the example which changed the structure of the evaporator unit 20 as shown in the whole block diagram of FIG. 9, and the typical perspective view of FIG. 10 with respect to 1st Embodiment. That is, in the first embodiment, the example in which the outflow side evaporator 20c is provided in both the upwind heat exchanger 23 and the downwind heat exchanger 24 has been described. However, in this embodiment, the outflow side evaporator 20c is abolished. is doing.

  More specifically, in the evaporator unit 20 of the present embodiment, as shown in FIG. 10, the first separator 23f, the second separator 23g, and the leeward side of the lower tank portion 23d of the windward heat exchanger 23 The first separator 24f in the lower tank portion 24d of the heat exchanger 24 is eliminated. Furthermore, the 2nd separator 24g is arrange | positioned in the 2nd space 242 in which the exit side of the ejector 21 is opening among the upper side tank parts 24c of the leeward side heat exchanger 24. FIG.

  And the gas-liquid separation space which isolate | separates the gas-liquid of the refrigerant | coolant which flowed out from the ejector 21 is comprised by the lower side space divided by the 2nd separator 24g among the 2nd space 242c of the leeward side heat exchanger 24. . In other words, in the present embodiment, the same gas-liquid separator 22 as that in the first embodiment is formed by the upper tank portion 24 c of the leeward heat exchanger 24.

  In the gas-liquid separator 22 of the present embodiment, since the first separator 24f in the lower tank portion 24d is eliminated, the liquid-phase refrigerant outlet hole 22a that functions as a decompression mechanism is also eliminated. Therefore, the inlet hole of the tube 24a connected to the lower space of the upper tank portion 24c is used as a pressure reducing mechanism. Of course, a fixed throttle such as an orifice as a pressure reducing mechanism may be disposed in the inlet hole of the tube 24a.

  The gas-phase refrigerant outlet hole 22b is provided in the same manner as in the first embodiment, and communicates with the second space 232 of the windward heat exchanger 23. Further, the lower tank portion 23d of the windward side heat exchanger 23 forms one internal space 230b as in the second embodiment. Similarly, the lower tank portion 24d of the leeward heat exchanger 24 also forms one internal space 240b without being partitioned by the third and fourth spaces 243 and 244.

  Therefore, in the present embodiment, in the heat exchange core portion 24e of the leeward heat exchanger 24, a region extending from the second space 242 to the internal space 240b and a region extending from the internal space 240b to the first space 241, that is, a heat exchange core. The entire area of the part 24e functions as the suction side evaporation part 20d. Further, in the heat exchange core portion 23e of the windward side heat exchanger 23, a region extending from the second space 231 to the internal space 230b and a region extending from the internal space 230b to the first space 231, that is, the entire region of the heat exchange core portion 23e. Functions as the sensible heat exchanger 20e.

  In the present embodiment, the volumes of the second spaces 232 and 242 of both the heat exchangers 23 and 24 are approximately equal to the volumes of the first spaces 231 and 241. The overall configuration and operation of the other evaporator units 20 and the ejector refrigeration cycle 10 are the same as those in the first embodiment.

  Therefore, when the ejector-type refrigeration cycle 10 of this embodiment is operated, even the evaporator unit 20 having the sensible heat exchanger 20e is blown out from the evaporator unit 20 as shown in the temperature distribution diagram of FIG. The temperature distribution of the blast air can be suppressed.

  FIG. 11 is a graph corresponding to FIG. 4 of the first embodiment. Furthermore, also in the evaporator unit 20 of this embodiment, the same size reduction effect and mountability improvement effect as in the first embodiment can be obtained.

(Fifth embodiment)
This embodiment demonstrates the example which changed the structure of the evaporator unit 20 as shown in the whole block diagram of FIG. 12, and the typical perspective view of FIG. 13 with respect to 1st Embodiment. That is, in the first embodiment, the example in which the sensible heat exchange unit 20e and the outflow side evaporation unit 20c are provided in the windward heat exchanger 23 has been described. However, in this embodiment, the sensible heat exchange is performed in the windward heat exchanger 23. An example in which the section 20e, the outflow side evaporation section 20c, and the suction side evaporation section 20d are provided will be described.

  More specifically, in the evaporator unit 20 of the present embodiment, as shown in FIG. 13, a plurality of first separators 23f and 24f are arranged inside the windward side heat exchanger 23 and the leeward side heat exchanger 24. Thus, the upper tank portions 23c and 24c and the lower tank portions 23d and 24d of both the heat exchangers 23 and 24 are partitioned into a plurality of spaces.

  Specifically, one first separator 24f is arranged in the internal space of the upper tank portion 24c of the leeward heat exchanger 24, and the first space on one end side in the longitudinal direction on the side where the ejector 21 is arranged. 241 and a second space 242 on the other end side. In addition, two first separators 24f are arranged in the internal space of the lower tank portion 24d, and the fourth to sixth spaces 244 to 246 are sequentially arranged from one end in the longitudinal direction on the side where the ejector 21 is arranged. It is partitioned.

  Further, the second separator 24g extending in the longitudinal direction of the lower tank portion 24d is disposed in the fifth space 245 at the central portion in the longitudinal direction, and the fifth space 245 is partitioned into an upper space and a lower space. The lower space of the fifth space 245 constitutes the same gas-liquid separation space as in the first embodiment. Therefore, the gas-liquid separator 22 of the present embodiment is formed by the lower tank portion 24d of the leeward heat exchanger 24.

  Further, the second separator 24g of the present embodiment is not provided with a communication hole 241g that allows the upper space and the lower space to communicate with each other. On the other hand, among the first separators 24f disposed in the lower tank portion 24d, the separator 24f that partitions the fifth space 245 and the sixth space 246 is formed with a communication hole, and the bottom of the fifth space 245 The side space (that is, the gas-liquid separation space) and the sixth space 246 communicate with each other.

  Next, two first separators 23f are arranged in the internal space of the upper tank portion 23c of the windward heat exchanger 23, and the first, second, second, in order from one end side where the ejector 21 is arranged. It is partitioned into three spaces 231, 232 and 233. In addition, two first separators 23f are disposed in the internal space of the lower tank portion 23d, and the fourth, fifth, and sixth spaces 234 and 235 are sequentially arranged from one end side on the side where the ejector 21 is disposed. 236.

  And the 3rd space 233 of the leeward side heat exchanger 23 and the 2nd space 242 of the leeward side heat exchanger 24 communicate directly via the communication holes formed in the wall surfaces of both the upper tank portions 23c and 24c. ing. Therefore, the refrigerant that has flowed out of the ejector 21 flows into both the third space 233 of the upwind heat exchanger 23 and the second space 242 of the leeward heat exchanger 24.

  Further, the sixth space 236 of the windward side heat exchanger 23 and the sixth space 246 of the leeward side heat exchanger 24 are directly communicated with each other through communication holes formed in the wall surfaces of both the upper tank portions 23c and 24c. ing. Accordingly, the refrigerant that has flowed out of the tube 23a group connecting the third space 233 and the sixth space 236 of the windward heat exchanger 23 and the second space 242 and the sixth space 246 of the leeward heat exchanger 24 are connected. The refrigerant that has flowed out of the tube 24a group merges in the sixth spaces 236 and 246 of both lower tank portions 23d and 24d.

  Further, the gas-phase refrigerant outlet hole 22 b of the gas-liquid separator 22 formed by the lower space of the fifth space 245 of the leeward heat exchanger 24 communicates with the fifth space 235 of the leeward heat exchanger 23. Yes. Further, the first separator 24f that partitions the fourth space 244 and the fifth space 245 of the leeward heat exchanger 24 is formed with a liquid-phase refrigerant outlet hole 22a of the gas-liquid separator 22 similar to the first embodiment. ing.

  The fourth space 244 of the leeward heat exchanger 24 and the upper space of the fifth space 245 communicate with each other through a communication hole formed in the first separator 24f, and the fourth space 244 of the leeward heat exchanger 24 communicates with the fourth space 244 of the leeward heat exchanger 24. The fourth space 234 of the windward side heat exchanger 23 is in direct communication via communication holes formed in the wall surfaces of the lower tank portions 23d and 24d.

  Therefore, the refrigerant that has flowed out of the liquid-phase refrigerant outlet hole 22a of the gas-liquid separator 22 flows into the fourth space of the leeward heat exchanger 24, the upper space of the fifth space of the leeward heat exchanger 24, and the windward heat. It flows into the fourth space of the exchanger 23. In addition, the second space 232 of the upwind heat exchanger 23 communicates with the refrigerant outlet 20 b of the evaporator unit 20.

  Further, the first space 231 of the leeward heat exchanger 23 and the first space 241 of the leeward heat exchanger 24 are directly communicated with each other through communication holes formed in the wall surfaces of both the upper tank portions 23c and 24c. Yes. Therefore, the refrigerant that has flowed out from the tube 23 a group connecting the fourth space 234 and the first space 231 of the windward heat exchanger 23 flows into the first space 241 of the leeward heat exchanger 24.

  That is, in the present embodiment, the region from the third space 233 to the sixth space 236 in the heat exchange core portion 23e of the windward heat exchanger 23 is the heat exchange core portion 24e of the leeward heat exchanger 24. The region from the second space 242 to the sixth space 246 functions as the outflow side evaporation unit 20c.

  Further, among the heat exchange core portion 23e of the windward side heat exchanger 23, the fourth space among the region extending from the fourth space 234 to the first space 231 and the heat exchange core portion 24e of the leeward side heat exchanger 24 is provided. A region from 234 to the first space 231 and a region from the upper space of the fifth space 235 to the first space 231 function as the suction side evaporation unit 20d.

  Furthermore, the area | region from the 5th space 235 to the 2nd space 232 among the heat exchange core parts 23e of the windward side heat exchanger 23 functions as the sensible heat exchange part 20e. The overall configuration and operation of the other evaporator units 20 and the ejector refrigeration cycle 10 are the same as those in the first embodiment.

  Therefore, when the ejector refrigeration cycle 10 of this embodiment is operated, even the evaporator unit 20 having the sensible heat exchanger 20e is blown out from the evaporator unit 20 as shown in the temperature distribution diagram of FIG. The temperature distribution of the blast air can be suppressed. FIG. 14 is a graph corresponding to FIG. 4 of the first embodiment.

  That is, according to this embodiment, the suction side evaporation unit 20d, the sensible heat exchange unit 20e, and the outflow side evaporation unit 20c are provided in the windward side heat exchanger 23, and the suction side evaporation unit 20d and the outflow side evaporation unit 20c are provided on the leeward side. Provided in the heat exchanger 24, and when viewed from the air flow direction, the suction side evaporation units 20d, the sensible heat exchange unit 20e, the suction side evaporation unit 20d, and the outflow side evaporation unit 20c are superposed with each other. Are arranged as follows.

  Therefore, the air cooled by the sensible heat exchange unit 20e having the highest temperature among the air cooled by the units 20c, 20d, and 20e can be further cooled by the suction side evaporation unit 20d. Thereby, as shown by the thick solid line in FIG. 6, the temperature between the temperature of the blown air blown from the suction side evaporator 20d of the leeward heat exchanger 24 and the temperature of the blown air blown from the outflow side evaporator 20c. The difference can be reduced.

  As a result, the temperature distribution of the air blown into the space to be cooled can be suppressed as the entire evaporator unit 20. Furthermore, also in the evaporator unit 20 of this embodiment, the same size reduction effect as the first embodiment can be 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.

  (1) In the above-described embodiment, so-called tank-and-tube heat exchangers are employed as the windward side heat exchanger 23 and the leeward side heat exchanger 24, and the gas-liquid separator is provided by the tank portions 23c ... 24d. Although the example in which 22 is formed has been described, the gas-liquid separator 22 may be configured by a member different from the tank portions 23c.

  In this case, for example, the gas-liquid separator 22 may be formed in a shape extending in parallel with the longitudinal direction of the tank portions 23c... 24d and joined to the tank portions 23c. The gas-liquid separator 22 may be joined to the side of the windward side heat exchanger 23 or the leeward side heat exchanger 24 in a shape extending in parallel with the longitudinal direction of the tubes 23a and 24a.

  (2) In the above-described embodiment, tank-and-tube heat exchangers are adopted as the windward side heat exchanger 23 and the leeward side heat exchanger 24, and the tank portions 23c of both the heat exchangers 23, 24 are used. Although an example in which at least a part of 24d is formed by the same member and integrated has been described, of course, both heat exchangers 23 and 24 are composed of different heat exchangers, and each heat exchanger is brazed. For example, they may be integrated by joining means such as bolts or mechanical engagement means such as bolt fastening.

  Further, the upwind heat exchanger 23 and the downwind heat exchanger 24 are not limited to tank-and-tube heat exchangers, and other types of heat exchangers can be employed. For example, a laminated heat exchanger in which a plurality of plate-like tube members and heat exchange fins are laminated may be adopted.

  In addition, this plate-like tube member is provided with an uneven portion on the plane of a plate-like plate formed of a metal having excellent heat conductivity (in this embodiment, aluminum), and a pair of plates are aligned in the middle. It is formed by joining and a tank part is formed in the longitudinal direction both ends of a tube and a tube.

  Therefore, the tube 23a for the windward side heat exchanger 23 and the tube 24a for the leeward side heat exchanger 24 are formed on one plate member so that these tubes 23a and 24a do not communicate with each other. One stacked heat exchanger can be functionally divided into two heat exchangers, an upwind heat exchanger 23 and a downwind heat exchanger 24.

  Furthermore, as a heat exchanger type, a serpentine heat exchanger configured by bending one tube in a meandering manner and arranging heat exchange fins between the tubes may be adopted.

  (3) In the above-described embodiment, the evaporator unit 20 is used to cool the air (gas) blown into the space to be cooled. As the fluid cooled by the evaporator unit 20, for example, in-vehicle You may cool a secondary heat medium like cooling water, such as an electric equipment. Further, a secondary heat medium tube through which the secondary heat medium passes is provided in each tank portion 23c... 24c or each heat exchange portion 23e, 24e of the evaporator unit 20, and both the air and the secondary heat medium are provided. It may be cooled.

  (4) In the ejector refrigeration cycle 10 of the above-described embodiment, the refrigerant that has flowed out of the high-pressure side refrigerant flow path 13a of the internal heat exchanger 13 is caused to flow into the evaporator unit 20, but the cycle configuration of the ejector refrigeration cycle Is not limited to this. For example, the internal heat exchanger 13 may be eliminated, or an expansion valve that decompresses and expands the refrigerant may be disposed in the refrigerant flow path from the outlet side of the radiator 12 to the refrigerant inlet 20a of the evaporator unit 20.

  Furthermore, if a temperature type expansion valve whose valve opening is adjusted so that the degree of superheat of the refrigerant sucked by the compressor 11 is a predetermined degree of superheat is adopted as the expansion valve, the liquid compression of the compressor 11 is performed. The problem can be avoided. In this case, the expansion valve may be integrally attached to the ejector 21 or the like as a constituent device of the evaporator unit 20.

  (5) In the above-described embodiment, an example in which a normal chlorofluorocarbon refrigerant is employed as the refrigerant of the ejector refrigeration cycle 10 has been described, but the type of refrigerant is not limited to this. For example, a hydrocarbon refrigerant or carbon dioxide may be used. Furthermore, the evaporator unit 20 of the present invention may be applied to a supercritical refrigeration cycle in which the high-pressure side refrigerant pressure exceeds the critical pressure of the refrigerant.

  (6) In the above embodiment, the ejector 21 is exemplified by a fixed ejector having the nozzle portion 21a having a constant passage area. However, the ejector 21 may be a variable ejector having a variable nozzle portion capable of adjusting the passage area. It may be used. As a specific example of the variable nozzle portion, for example, a mechanism may be used in which a needle is inserted into the passage of the variable nozzle portion and the passage area is adjusted by controlling the position of the needle with an electric actuator.

  (7) In each of the above-described embodiments, the example in which the evaporator unit 20 of the present invention is applied to the ejector refrigeration cycle 10 mounted on the vehicle air conditioner has been described. However, the application of the evaporator unit 20 of the present invention is described. Is not limited to this. For example, the present invention may be applied to a stationary ejector refrigeration cycle such as a commercial refrigeration / refrigeration apparatus, a vending machine cooling apparatus, and a showcase with a refrigeration function.

  (8) In the above-described embodiment, the windward heat exchanger 23 and the leeward heat exchanger 24 are configured as indoor heat exchangers, and the radiator 12 is configured as an outdoor heat exchanger that radiates heat to the atmosphere side. However, conversely, the windward heat exchanger 23 and the leeward heat exchanger 24 are configured as outdoor heat exchangers that absorb heat from a heat source such as the atmosphere, and the radiator 12 heats a refrigerant to be heated such as air or water. The evaporator unit 20 of the present invention may be applied to a heat pump cycle configured as an indoor heat exchanger.

DESCRIPTION OF SYMBOLS 20 Evaporator unit 20c Outflow side evaporation part 20d Suction side evaporation part 20e Sensible heat exchange part 21 Ejector 21a Nozzle part 21c Refrigerant suction port 22 Gas-liquid separator 22a Liquid phase refrigerant outlet hole 23 Upwind heat exchanger 23a, 24b Tube 23c 24c Upper tank part 23d, 24d Lower tank part 24 Downward heat exchanger

Claims (5)

The refrigerant sucked from the refrigerant suction port (21c) by the flow of the high-speed jet refrigerant jetted from the nozzle part (21a) for decompressing the refrigerant, and the suction refrigerant sucked from the refrigerant suction port (21c) and the jetted refrigerant And an ejector (21) for increasing the pressure by mixing
A gas-liquid separator (22) for separating the gas-liquid of the refrigerant flowing out of the ejector (21);
An upwind heat exchanger (23) disposed on the upwind side of the flow of air that is exchanged with the refrigerant and blown into the space to be cooled;
A leeward heat exchanger (24) disposed on the leeward side of the air flow with respect to the leeward heat exchanger (23),
The leeward heat exchanger (23) is provided with a sensible heat exchanger (20e) for exchanging heat between the gas-phase refrigerant flowing out of the gas-liquid separator (22) and the air,
In the leeward heat exchanger (24), the liquid-phase refrigerant that has flowed out of the gas-liquid separator (22) is evaporated by exchanging heat with the air, and is drawn out to the refrigerant suction port (21c) side. A side evaporator (20d) is provided;
The evaporator unit, wherein the sensible heat exchange part (20e) and the suction side evaporation part (20d) are arranged so as to overlap each other when viewed from the air flow direction. The refrigerant sucked from the refrigerant suction port (21c) by the flow of the high-speed jet refrigerant jetted from the nozzle part (21a) for decompressing the refrigerant, and the suction refrigerant sucked from the refrigerant suction port (21c) and the jetted refrigerant And an ejector (21) for increasing the pressure by mixing
A gas-liquid separator (22) for separating the gas-liquid of the refrigerant flowing out of the ejector (21);
An upwind heat exchanger (23) disposed on the upwind side of the flow of air that is exchanged with the refrigerant and blown into the space to be cooled;
A leeward heat exchanger (24) disposed on the leeward side of the air flow with respect to the leeward heat exchanger (23),
The leeward heat exchanger (23) is provided with a sensible heat exchanger (20e) for exchanging heat between the gas-phase refrigerant flowing out of the gas-liquid separator (22) and the air,
In the leeward heat exchanger (24), the liquid-phase refrigerant that has flowed out of the gas-liquid separator (22) is evaporated by exchanging heat with the air, and is drawn out to the refrigerant suction port (21c) side. Side evaporating section (20d) and outflow side evaporating section (20c) for evaporating the refrigerant flowing out from the ejector (21) by exchanging heat with the air to flow out to the gas-liquid separator (22) inlet side Is provided,
At least one of the sensible heat exchange part (20e) and the suction side evaporation part (20d) and the outflow side evaporation part (20c) is superposed with each other when viewed from the air flow direction. An evaporator unit characterized in that it is arranged. Furthermore, a part of the outflow side evaporation section (20c) is provided in the upwind heat exchanger (23),
The sensible heat exchange part (20e) and the suction side evaporation part (20d) are arranged to overlap each other when viewed from the air flow direction,
The outflow side evaporator (20c) provided in the windward side heat exchanger (23) and the outflow side evaporator (20c) provided in the leeward side heat exchanger (24) are arranged in the direction of air flow. The evaporator unit according to claim 2, wherein the evaporator unit is disposed so as to be polymerized with each other when viewed from the side. At least one of the windward side heat exchanger (23) and the leeward side heat exchanger (24) includes a plurality of tubes (23a, 24a) through which a refrigerant that exchanges heat with the air flows and the plurality of tubes ( 23a, 24a) and tank portions (23c, 23d, 24c, 24d) that perform the function of distributing and collecting refrigerant.
The evaporator unit according to any one of claims 1 to 3, wherein the gas-liquid separator (22) is formed by the tank portion (23c, 23d, 24c, 24d).   The decompression mechanism (22a) for depressurizing the liquid phase refrigerant flowing out of the gas-liquid separator (22) is disposed inside the tank portion (23c, 23d, 24c, 24d). Item 5. The evaporator unit according to Item 4.

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