JP6597458B2 - Refrigerant evaporator - Google Patents

Description

  The present invention relates to a refrigerant evaporator that exchanges heat between a fluid to be cooled and a refrigerant.

  Vehicle air conditioners using a refrigeration cycle are widely used. In the refrigeration cycle, the compressor is driven by the output of an engine that generates a driving force for running the vehicle. The refrigerant pumped by the compressor flows through an internal flow path such as a refrigerant evaporator provided in the refrigeration cycle, and exchanges heat with air. The vehicle air conditioner can adjust the temperature of the air in the vehicle interior by supplying the air thus heat-exchanged into the vehicle interior.

  In such a refrigeration cycle, the compressor cannot be driven when the engine is stopped at a so-called idling stop or the like. Thus, studies are underway to continuously cool the air in the refrigerant evaporator even when the compressor is stopped.

  For example, Patent Document 1 describes a refrigerant evaporator including a cold storage container. This cold storage container has a space for storing the cold storage material therein, and is disposed in the heat exchange section. While the compressor is being driven, the temperature of the cold storage material decreases by exchanging heat with the low-temperature refrigerant supplied to the refrigerant evaporator (hereinafter, this is also referred to as “accumulating cold”). On the other hand, while the compressor is stopped, the cool storage material absorbs heat from the air to cool the air.

JP 2010-91250 A

  In the refrigeration cycle, a compressor is generally arranged downstream of the refrigerant evaporator. When liquid phase refrigerant is supplied to the compressor, an excessive load is generated on the compressor in an attempt to compress the liquid phase refrigerant.

  Therefore, the refrigerant supplied from the refrigerant evaporator to the compressor is preferably in a completely vaporized state. For this reason, in the refrigerant evaporator, a portion called a “superheat zone” or the like is provided in the vicinity of the downstream end of the internal flow path. In the superheat region, the refrigerant vaporized on the upstream side of the superheat region is further heated to raise the temperature, and the refrigerant is surely made into a gas phase.

  However, in the refrigerant evaporator described in Patent Document 1, there is a problem that by providing this superheat region, cooling of the air by the cool storage material while the compressor is stopped is hindered. Specifically, the cold storage material receives heat from the high-temperature refrigerant in the superheat region while the compressor is driven, and the cold heat cannot be stored sufficiently, and the air cannot be sufficiently cooled while the compressor is stopped. There was a problem.

  The present invention has been made in view of such problems, and an object thereof is to provide a refrigerant evaporator capable of sufficiently storing cold heat in a cold storage material while reliably evaporating the refrigerant in a superheat region. There is to do.

In order to solve the above-described problems, a refrigerant evaporator according to the present invention is a refrigerant evaporator (1) that performs heat exchange between a fluid to be cooled and a refrigerant, and includes a plurality of winds arranged with a gap therebetween. An upwind core section (11) having an upper tube (11c) for exchanging heat between the refrigerant flowing in the plurality of upwind tubes and the fluid to be cooled, and a plurality of downwind sides arranged with a gap between each other A tube (21c), arranged to overlap the windward core portion downstream of the windward core portion in the flow direction of the fluid to be cooled, and the refrigerant flowing in the plurality of leeward tubes and the windward core portion. A leeward core (21) that exchanges heat with the cooled fluid that has passed through, and a communication channel that guides the refrigerant flowing out from the downstream end of the leeward tube to flow into the upstream end of the leeward tube ( 13, 23, 33) and the cold storage material inside ( 1) is accommodated, and is disposed in a gap between adjacent windward tubes and a gap between adjacent leeward tubes, and is disposed so as to straddle the windward core portion and the leeward core portion. A cold storage case (40). The windward side tube, the gas-liquid mixed region and the refrigerant in the refrigerant and the vapor phase of a liquid phase you mixed with (GL), Luz Pahito zone refrigerant is heated in the vapor phase and (SH), are formed, the gas when the boundary between the liquid mixed region and superheat region and superheat boundary (SH1), cold storage case is disposed adjacent to the windward-side tube so as to face the gas-liquid mixed zone and superheating zone,蓄 cold The material is accommodated only in the portion of the cold storage case that is disposed closer to the gas-liquid mixture area than the superheat boundary.

  In the host machine configuration, the regenerator material is accommodated only in the part of the regenerator case corresponding to the gas-liquid mixture region side of the superheat boundary. Thereby, it can suppress that a cool storage material receives heat from the high-temperature refrigerant | coolant of a superheat area, and can fully store cold heat in a cool storage material.

  ADVANTAGE OF THE INVENTION According to this invention, the refrigerant | coolant evaporator which can fully store cold heat in a cool storage material can be provided, ensuring a vaporization of a refrigerant | coolant by a superheat area.

It is a perspective view which shows the refrigerant evaporator which concerns on embodiment. It is a side view which shows the refrigerant evaporator of FIG. It is a disassembled perspective view which shows the flow of the refrigerant | coolant in the refrigerant evaporator of FIG. It is a perspective view which shows the partition member of FIG. It is explanatory drawing which shows the windward evaporation part, windward tube, and cool storage case of FIG.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. In order to facilitate the understanding of the description, the same constituent elements in the drawings will be denoted by the same reference numerals as much as possible, and redundant description will be omitted.

  First, the configuration of the refrigerant evaporator 1 will be described with reference to FIGS. 1 to 4. The refrigerant evaporator 1 is a heat exchanger that uses air as a fluid to be cooled. The refrigerant evaporator 1 includes an upwind evaporator 10, a downwind evaporator 20, an intermediate tank 33, and a plurality of cold storage cases 40.

  The windward evaporator 10 includes a windward core part 11, a windward distribution tank part 13, and a windward collecting tank part 12.

  As shown in FIG. 1, the windward core portion 11 is configured by a stacked body in which a plurality of windward tubes 11c and a plurality of fins 11d are alternately stacked in the horizontal direction. The windward side tube 11c has a flat cross section and extends in the vertical direction, and a flow path for flowing the refrigerant is formed inside. The fin 11d is a corrugated fin, and is formed by bending a thin metal plate. The fin 11d is arrange | positioned between the adjacent windward side tubes 11c, and is joined to the flat surface among the outer surfaces of the windward side tube 11c. In addition, side plates 11e are arranged at both ends of the laminate composed of the plurality of windward tubes 11c and the plurality of fins 11d (hereinafter, this direction is also simply referred to as “stacking direction”). The upper core part 11 is reinforced. 2 and 3, illustration of the windward side tubes 11c, the fins 11d, and the side plates 11e that constitute the windward side core portion 11 is omitted.

  As shown in FIG. 3, the windward core portion 11 includes a third core portion 11a and a fourth core portion 11b. The 3rd core part 11a is a part of several windward side tubes 11c, and is comprised by the group of windward side tubes 11c arranged so that it may form one row | line | column. The fourth core portion 11b is a remaining portion of the plurality of windward tubes 11c, and is configured by a group of windward tubes 11c arranged to form one row. The 3rd core part 11a and the 4th core part 11b are arrange | positioned so that it may adjoin in the lamination direction. When the refrigerant evaporator 1 is viewed along the X direction, which is the direction in which air flows, the third core portion 11a is configured by a tube group disposed on the right side in the stacking direction, and the fourth core portion 11b is in the stacking direction. It consists of a group of tubes arranged on the left side. That is, part of the air flowing in the X direction passes through the third core part 11a, and the other part passes through the fourth core part. Each of the third core portion 11a and the fourth core portion 11b has a wide shape in which the dimension in the stacking direction is larger than the dimension in the X direction.

  The windward distribution tank unit 13 is disposed below the windward core unit 11. The windward distribution tank unit 13 is a cylindrical body whose both ends are closed, and a flow path through which a refrigerant flows is formed inside. A plurality of through holes (not shown) are formed in the upper part of the windward distribution tank unit 13. Lower end portions of a plurality of upwind tubes 11c constituting the upwind core portion 11 are inserted into and joined to the through holes. That is, the windward distribution tank unit 13 is configured such that the flow path inside thereof communicates with the plurality of windward tubes 11 c of the windward core unit 11. Thereby, the windward distribution tank unit 13 functions as a distribution unit for distributing the refrigerant to the plurality of windward tubes 11 c constituting the windward core unit 11.

  As shown in FIG. 3, a partition plate 13 c is disposed inside the upwind distribution tank unit 13 and at the center position in the longitudinal direction. The partition plate 13c partitions the internal flow path of the windward distribution tank unit 13 into a first distribution unit 13a and a second distribution unit 13b. The 1st distribution part 13a is the space connected to the some upwind tube 11c which comprises the 3rd core part 11a. The 1st distribution part 13a distributes a refrigerant | coolant to the some upwind tube 11c which comprises the 3rd core part 11a. The 2nd distribution part 13b is the space connected to the some upwind tube 11c which comprises the 4th core part 11b. The 2nd distribution part 13b distributes a refrigerant | coolant to the some upwind tube 11c which comprises the 4th core part 11b. A first distribution unit communication port 131 and a second distribution unit communication port 132 are formed on the side surface of the windward distribution tank unit 13 on the intermediate tank unit 33 side. The 1st distribution part communication port 131 penetrates the pipe wall of the windward distribution tank part 13, and connects the inside and outside of the 1st distribution part 13a. The 2nd distribution part communication port 132 penetrates the pipe wall of the windward distribution tank part 13, and connects the inside and outside of the 2nd distribution part 13b.

  The windward collecting tank 12 is disposed above the windward core 11. The windward collecting tank portion 12 is a cylindrical body, and a flow path through which the refrigerant flows is formed inside. When viewed along the X direction, the windward side collecting tank portion 12 is closed at the left end and formed with a refrigerant outlet 12a at the right end. The refrigerant outlet 12a leads the refrigerant from the inside of the windward collecting tank portion 12 to the suction side of a compressor (not shown). A plurality of through holes (not shown) are formed at the bottom of the windward collecting tank 12. Upper end portions of a plurality of windward tubes 11c constituting the windward core portion 11 are inserted into and joined to the through holes. That is, the windward side collective tank unit 12 is configured such that the flow path inside thereof communicates with the plurality of windward side tubes 11 c of the windward side core unit 11. Thereby, the windward collecting tank unit 12 functions as a collecting unit for collecting the refrigerant flowing out from the plurality of windward tubes 11 c of the windward core unit 11.

  The leeward evaporator 20 is arranged so as to overlap with the leeward evaporator 10 when viewed along the X direction. The leeward side evaporation unit 20 includes a leeward side core portion 21, a leeward side distribution tank portion 22, and a leeward side collecting tank portion 23.

  As shown in FIG. 1, the leeward core portion 21 is configured by a laminated body in which a plurality of leeward tubes 21 c and a plurality of fins 21 d are alternately laminated in the horizontal direction. The leeward side tube 21c has a flat cross section and extends in the vertical direction, and a flow path for flowing the refrigerant is formed inside. The fins 21d are corrugated fins and are formed by bending a thin metal plate. The fins 21d are disposed between the adjacent leeward tubes 21c, and are joined to a flat surface of the outer surfaces of the leeward tubes 21c. In addition, side plates 21e are arranged at both ends in the stacking direction of the laminate composed of the plurality of leeward tubes 21c and the plurality of fins 21d to reinforce the leeward core portion 21. 2 and 3, illustration of the leeward side tubes 21c, the fins 21d, and the side plates 21e constituting the leeward side core portion 21 is omitted.

  As shown in FIG. 3, the leeward core portion 21 includes a first core portion 21 a and a second core portion 21 b. The 1st core part 21a is a part of several leeward side tubes 21c, and is comprised by the group of leeward side tubes 21c arranged so that it may form one row. The second core portion 21b is a remaining portion of the plurality of leeward tubes 21c, and is configured by a group of leeward tubes 21c arranged in one row. The 1st core part 21a and the 2nd core part 21b are arrange | positioned so that it may adjoin in the lamination direction. When the refrigerant evaporator 1 is viewed along the X direction in which air flows, the first core portion 21a is configured by a tube group disposed on the right side in the stacking direction, and the second core portion 21b is disposed on the left side in the stacking direction. It is comprised by the tube group made. Further, when the refrigerant evaporator 1 is viewed along the X direction, the first core portion 21a is disposed so as to overlap with the third core portion 11a, and the second core portion 21b is disposed so as to overlap with the fourth core portion 11b. ing. As a result, the air flowing in the X direction passes through the first core portion 21a after part of the air passes through the third core portion 11a, while the second part passes through the fourth core portion 11b. It passes through the core part 21b. Each of the first core portion 21a and the second core portion 21b has a wide shape in which the dimension in the stacking direction is larger than the dimension in the X direction.

  The leeward distribution tank unit 22 is disposed above the leeward core unit 21. The leeward side distribution tank unit 22 is a cylindrical body, and a flow path through which the refrigerant flows is formed inside. When viewed along the X direction, the leeward side distribution tank section 22 is closed at the left end and formed with a refrigerant inlet 22a at the right end. The refrigerant inlet 22a introduces a low-pressure refrigerant decompressed by an unillustrated expansion valve. A plurality of through holes (not shown) are formed at the bottom of the leeward distribution tank unit 22. Upper end portions of a plurality of leeward tubes 21c constituting the leeward core portion 21 are inserted and joined to the through holes. That is, the leeward side distribution tank part 22 is configured such that the flow path inside thereof communicates with the plurality of leeward side tubes 21 c of the leeward side core part 21. Thereby, the leeward side distribution tank part 22 functions as a distribution part for distributing the refrigerant to the plurality of leeward side tubes 21 c constituting the leeward side core part 21.

  The leeward side collecting tank portion 23 is disposed below the leeward side core portion 21. The leeward side collecting tank portion 23 is a cylindrical body whose both ends are closed, and a flow path through which a refrigerant flows is formed inside. A plurality of through holes (not shown) are formed in the upper part of the leeward side collecting tank portion 23. Lower end portions of a plurality of leeward tubes 21c constituting the leeward core portion 21 are inserted into and joined to the through holes. That is, the leeward side collective tank portion 23 is configured such that the flow path inside thereof communicates with the plurality of leeward side tubes 21c.

  A partition plate 23c is arranged inside the leeward side collecting tank portion 23 and at the center position in the longitudinal direction. The partition plate 23c divides the internal flow path of the leeward side collecting tank portion 23 into a first collecting portion 23a and a second collecting portion 23b. The first collecting portion 23a is a space that communicates with the plurality of leeward side tubes 21c constituting the first core portion 21a. The 1st gathering part 23a collects the refrigerant which flowed out from a plurality of leeward side tubes 21c which constitute the 1st core part 21a. The second collecting portion 23b is a space communicating with the plurality of leeward tubes 21c constituting the second core portion 21b. The second collecting portion 23b collects the refrigerant that has flowed out from the plurality of leeward tubes 21c constituting the second core portion 21b. That is, the leeward side collecting tank portion 23 functions as a collecting portion that separately collects the refrigerant flowing out from the first core portion 21a and the refrigerant flowing out from the second core portion 21b.

  A first collecting portion communication port 231 and a second collecting portion communication port 232 are formed on the side surface of the leeward collecting tank portion 23 on the intermediate tank portion 33 side. The first collecting portion communication port 231 passes through the tube wall of the leeward collecting tank portion 23 and communicates the inside and outside of the first collecting portion 23a. Further, the second collecting portion communication port 232 penetrates the tube wall of the leeward collecting tank portion 23 and communicates the inside and outside of the second collecting portion 23b.

  The intermediate tank unit 33 is provided between the windward distribution tank unit 13 of the windward evaporator 10 and the leeward collective tank unit 23 of the leeward evaporator 20. The intermediate tank part 33 is a cylindrical body in which a flow path through which a refrigerant flows is formed.

  As shown in FIG. 3, a partition member 34 is provided inside the intermediate tank portion 33. As shown in FIG. 4, the partition member 34 includes plate-like side plates 34a and 34b and a bottom plate 34c each having a predetermined thickness. The side plates 34 a and 34 b are arranged so as to be spaced from each other, and are curved so that one end thereof is along the inner wall surface of the intermediate tank portion 33. The bottom plate 34c extends so as to connect the other ends of the side plates 34a and 34b.

  The partition member 34 is provided in a portion near the upper part in the intermediate tank portion 33. The intermediate tank 33 is partitioned into a first passage 33 a and a second passage 33 b by the partition member 34.

  As shown in FIG. 3, the first passage 33 a is a space surrounded by the upper pipe wall of the intermediate tank portion 33, the side plates 34 a and 34 b and the bottom plate 34 c of the partition member 34. The volume of the first passage 33a is smaller than the volume of the second passage 33b.

  As shown in FIG. 3, the second passage 33 b is a portion formed around the first passage 33 a in the space in the intermediate tank portion 33. The second passage 33b has a throttle channel 33k. The throttle channel 33k is formed in the lower part of the intermediate tank 33 by the partition member 34. An end channel 33m is formed on the upstream side of the throttle channel 33k, and an end channel 33n is formed on the downstream side. The end channels 33m and 33n have a channel cross-sectional area larger than that of the throttle channel 33k.

  As shown in FIG. 3, a first communication port 331 and a second communication port 332 are formed on the side surface of the intermediate tank unit 33 and on the leeward side collecting tank unit 23 side. The first communication port 331 penetrates the tube wall of the intermediate tank portion 33 and communicates the inside and the outside of the first passage 33a. The second communication port 332 passes through the tube wall of the intermediate tank 33 and communicates with the inside and outside of the second passage 33b.

  In addition, a third communication port 333 and a fourth communication port 334 are formed on the side surface of the intermediate tank unit 33 on the windward distribution tank unit 13 side. The third communication port 333 passes through the tube wall of the intermediate tank portion 33 and communicates the inside and the outside of the second passage 33b. The fourth communication port 334 passes through the tube wall of the intermediate tank 33 and communicates with the inside and outside of the first passage 33a.

  The plurality of cool storage cases 40 are members having a flat cross section and extending in the vertical direction. The plurality of cool storage cases 40 are arranged at positions that are symmetric in the stacking direction. As will be described later with reference to FIG. 5, the cold storage case 40 has an accommodation space 42 formed therein. A cool storage material 41 is stored in the storage space 42. As the cold storage material 41, for example, paraffin can be used.

  The cold storage case 40 is disposed in a gap between the adjacent windward side tubes 11 c and 11 c of the windward side core part 11 and a gap between the adjacent leeward side tubes 21 c and 21 c of the leeward side core part 21. That is, the cold storage case 40 is disposed so as to straddle the leeward core portion 11 and the leeward core portion 21 as shown in FIG.

  Next, the flow of the refrigerant in the refrigerant evaporator 1 and the air cooling by the refrigerant flow will be described with reference to FIG.

  When the compressor is driven by receiving the output of an engine (not shown), the low-pressure refrigerant decompressed by an expansion valve (not shown) is supplied to the refrigerant evaporator 1 in a liquid phase state. As indicated by an arrow A, the refrigerant is introduced into the leeward distribution tank unit 22 from the refrigerant inlet 22a. This refrigerant is distributed inside the leeward side distribution tank part 22 and flows into the first core part 21a and the second core part 21b of the leeward side core part 21 as indicated by arrows B and C.

  The refrigerant that has flowed into the first core portion 21a and the second core portion 21b flows downward inside the plurality of leeward tubes 21c that constitute each of them. At this time, the refrigerant flowing inside the plurality of leeward tubes 21c exchanges heat with the air passing between the plurality of leeward tubes 21c in the X direction. As a result, part of the liquid-phase refrigerant evaporates and absorbs heat from the air, thereby cooling the air.

  The refrigerant flowing out from the lower end portion of the first core portion 21a flows into the first collecting portion 23a of the leeward collecting tank portion 23 and is collected as indicated by an arrow D. Further, the refrigerant flowing out from the lower end portion of the second core portion 21 b flows into the second collecting portion 23 b of the leeward collecting tank portion 23 and is collected as indicated by an arrow E.

  The refrigerant collected in the first collecting portion 23a is discharged from the first collecting portion 23a through the first collecting portion communication port 231 as indicated by an arrow F. This refrigerant flows into the first passage 33a through the first communication port 331. Further, the refrigerant collected in the second collecting portion 23b is discharged from the second collecting portion 23b through the second collecting portion communication port 232 as indicated by an arrow G. This refrigerant flows into the end flow path 33m of the second passage 33b via the second communication port 332.

  The refrigerant that has flowed into the end flow path 33m of the second passage 33b flows into the throttle flow path 33k so as to wrap around the first passage 33a. Since the throttle channel 33k has a smaller channel cross-sectional area than the end channel 33m, the flow rate of the refrigerant flowing into the throttle channel 33k increases. The refrigerant that has flowed through the throttle channel 33k at high speed flows into the end channel 33n on the downstream side. This refrigerant flows toward the third communication port 333.

  The refrigerant that has passed through the first passage 33a of the intermediate tank portion 33 is discharged from the first passage 33a through the fourth communication port 334 as indicated by an arrow H. The refrigerant flows toward the windward distribution tank unit 13 and flows into the second distribution unit 13b through the second distribution unit communication port 132.

  On the other hand, the refrigerant that has passed through the second passage 33b of the intermediate tank portion 33 is discharged from the second passage 33b through the third communication port 333 as indicated by an arrow I. The refrigerant flows toward the windward distribution tank unit 13 and flows into the first distribution unit 13a through the first distribution unit communication port 131.

  As indicated by the arrow K, the refrigerant that has flowed into the first distribution portion 13a flows from the lower end portion of the third core portion 11a. Specifically, the refrigerant in the first distribution unit 13a is distributed to the plurality of upwind tubes 11c constituting the third core unit 11a.

  The refrigerant that has flowed into the second distribution portion 13b flows from the lower end portion of the fourth core portion 11b as indicated by an arrow J. Specifically, the refrigerant in the second distribution unit 13b is distributed to the plurality of upwind tubes 11c constituting the fourth core unit 11b.

  That is, the upwind distribution tank unit 13, together with the leeward side collective tank unit 23 and the intermediate tank unit 33, communicates the refrigerant flowing out from the downstream end of the leeward side tube 21 c so as to flow into the upstream end of the upwind side tube 11 c. Functions as a road.

  The refrigerant that has flowed into the third core portion 11a and the fourth core portion 11b flows upward in the plurality of windward tubes 11c constituting each of them. At this time, the refrigerant flowing inside the plurality of windward tubes 11c exchanges heat with the air passing between the plurality of windward tubes 11c in the X direction. As a result, part of the liquid-phase refrigerant evaporates and absorbs heat from the air, thereby cooling the air.

  As indicated by arrows M and L, the refrigerant that has flowed out from the upper ends of the third core portion 11a and the fourth core portion 11b flows into and joins the inside of the windward collecting tank portion 12. As indicated by an arrow N, this refrigerant flows through the inside of the windward collecting tank unit 12 and flows out of the refrigerant evaporator 1 from the refrigerant outlet 12a. Thereafter, the refrigerant is supplied to the suction side of a compressor (not shown).

  As described above, in the configuration in which the refrigerant flows into the leeward distribution tank portion 22 from the refrigerant inlet 22a in the vicinity of the first core portion 21a, the flow rate of the refrigerant distributed to the first core portion 21a and the second core portion 21b. There will be a difference. That is, there is a tendency that a refrigerant having a larger flow rate is supplied to the first core portion 21a that is close to the refrigerant inlet 22a and into which the refrigerant easily flows, as compared to the second core portion 21b that is far from the refrigerant inlet 22a.

  When such a difference in the flow rate of the refrigerant occurs, the air passing through the first core portion 21a actively exchanges heat with the refrigerant as compared with the air passing through the second core portion 21b. For this reason, there is a possibility that the temperature distribution is biased in the air passing in the X direction.

  Therefore, the refrigerant evaporator 1 is configured so that the refrigerant from the leeward side collective tank unit 23 toward the upwind distribution tank unit 13 intersects the X direction as described above. That is, the refrigerant in the first collecting portion 23 a of the leeward collecting tank portion 23 is guided to the second distributing portion 13 b of the leeward distributing tank portion 13 through the intermediate tank portion 33. Further, the refrigerant in the second collecting portion 23 b of the leeward collecting tank portion 23 is guided to the first distributing portion 13 a of the leeward distributing tank portion 13 through the intermediate tank portion 33.

  Thus, by replacing the refrigerant so as to intersect the X direction, the flow rate of the refrigerant in which a part of the air passing through the first core portion 21a and the third core portion 11a exchanges heat, and the second core It becomes possible to reduce the difference between the flow rate of the refrigerant that exchanges heat with the other part of the air passing through the portion 21b and the fourth core portion 11b. As a result, it is possible to suppress an uneven temperature distribution in the air passing in the X direction.

  Further, in the regenerator case 40, it is arranged in a gap between the adjacent windward side tubes 11 c, 11 c of the windward side core part 11 and a gap between the adjacent leeward side tubes 21 c, 21 c of the leeward side core part 21. In the portion, heat exchange is performed between the cold storage material 41 and the low-pressure refrigerant with the tube wall of the cold storage case 40 interposed therebetween. Thereby, the temperature of the cool storage material 41 in the cool storage case 40 falls. That is, the cold storage material 41 stores cold heat during driving of the compressor.

  On the other hand, when the engine is stopped at the time of so-called idling stop or the like, the compressor cannot be driven, and the supply of the refrigerant to the refrigerant evaporator 1 is stopped. Therefore, the refrigerant stops flowing in the refrigerant evaporator 1 while the compressor is stopped.

  However, in the refrigerant evaporator 1, even when the compressor is stopped, the air can be cooled by the cold storage material 41 that has accumulated cold heat until then. That is, the cold storage material 41 having a low temperature exchanges heat with the refrigerant remaining inside the windward side tube 11c and the leeward side tube 21c with the tube wall of the cold storage case 40 interposed therebetween. Thereby, the refrigerant is cooled and the temperature is maintained at a relatively low value. By performing heat exchange between the refrigerant whose temperature is maintained in this way and air, the air is continuously cooled even when the compressor is stopped.

  Next, the inside of the windward side tube 11c and the cold storage case 40 will be described with reference to FIG. FIG. 5 shows the windward evaporator 10 viewed along the Y direction shown in FIG. Moreover, the cross section of the windward side tube 11c and the cross section of the cool storage case 40 are schematically shown on the right side of the windward side evaporator 10. FIG. 5 shows the windward side evaporator 10, the windward side tube 11 c, and the cold storage case 40 in a state where the compressor is being driven.

  As described above, the refrigerant 50 flows upward in the windward side tube 11 c of the windward side evaporator 10. The inside of the windward side tube 11c can be divided into three parts based on the state of the refrigerant 50 in the vertical direction. Specifically, the inside of the windward side tube 11c includes a liquid phase region LL in which only the liquid phase refrigerant 50 exists, a gas / liquid mixture region GL in which the liquid phase refrigerant 50 and the gas phase refrigerant 50 are mixed, It can be divided into a superheat region SH in which only the gas-phase refrigerant 50 exists. The boundary between the gas / liquid mixture region GL and the superheat region SH is referred to as a superheat boundary SH1.

  The refrigeration cycle including the refrigerant evaporator 1 is operated such that a superheat region SH is formed at the upper ends of the third core portion 11a and the fourth core portion 11b, which are the downstream ends of the windward side tube 11c. In the superheat region SH, the refrigerant 50 vaporized in the upstream gas-liquid mixture region GL is further heated by performing heat exchange with air. Thereby, the temperature of the refrigerant 50 rises in a gas phase state in the superheat region SH. The gas phase refrigerant 50 is supplied to a compressor disposed downstream of the refrigerant evaporator 1 in the refrigeration cycle. Thereby, it can suppress that an excessive load arises by compressing a liquid phase refrigerant in a compressor.

  The gas-phase refrigerant 50 flowing through the superheat region SH becomes high temperature by exchanging heat with air. If the cool storage material 41 stored in the storage space 42 of the cool storage case 40 receives heat from the high-temperature refrigerant 50, there is a possibility that the cool heat cannot be stored sufficiently. In this case, the refrigerant 50 inside the windward side tube 11c and the leeward side tube 21c cannot be cooled by the cold storage material 41 while the compressor is stopped. That is, it becomes impossible to properly cool the air by the refrigerant evaporator 1 while the compressor is stopped.

  Therefore, the regenerator material 41 accommodated in the accommodation space 42 of the regenerator case 40 is arranged such that the upper surface 411 is positioned below the superheat boundary SH1. Since the cold storage material 41 expands and contracts as the temperature changes, the position of the upper surface 411 also changes. The refrigeration cycle including the refrigerant evaporator 1 is operated under the condition of being located below the superheat boundary SH1 even when the upper surface 411 of the regenerator material 41 is located at the uppermost position.

  Thus, in the refrigerant evaporator 1, the cool storage material 41 is accommodated only in a part of the cool storage case 40 corresponding to the gas-liquid mixture region GL side with respect to the superheat boundary SH1. Thereby, it is possible to suppress the cold storage material 41 from receiving heat from the high-temperature refrigerant 50 in the superheat region SH and to sufficiently store the cold energy in the cold storage material 41.

  The plurality of cool storage cases 40 are arranged at symmetrical positions in the direction in which the plurality of windward side tubes 11c and the plurality of leeward side tubes 21c are arranged.

  According to this configuration, in the direction in which the plurality of leeward tubes 11c and the plurality of leeward tubes 21c are arranged (that is, the above-described stacking direction), the air that passes through the leeward core portion 11 and the leeward core portion 21 is evenly distributed. Can be cooled. Specifically, the cool storage material 41 in the cool storage case 40 cools the refrigerant 50 in the windward side tube 11 c and the leeward side tube 21 c to lower the temperature, and passes through the windward side core part 11 and the leeward side core part 21. The air is cooled by exchanging heat with the low-temperature refrigerant 50. As a result, it is possible to suppress the occurrence of uneven temperature distribution in the air.

  The leeward core portion 21 includes a first core portion 21a that exchanges heat between a part of the air that is the fluid to be cooled and a part of the refrigerant, another part of the air, and other refrigerants And a second core portion 21b that exchanges heat with a part. The windward core portion 11 is disposed so as to overlap the first core portion 21a in the air flow direction, and the third core portion 11a allows heat exchange between a part of the air and the other part of the refrigerant. The fourth core portion 11b is disposed so as to overlap the second core portion 21b in the air flow direction, and allows heat exchange between the other part of the air and a part of the refrigerant. The refrigerant evaporator 1 has a refrigerant inlet 22a in the vicinity of the first core portion 21a and is provided at the upstream ends of a plurality of leeward tubes 21c constituting the first core portion 21a and the second core portion 21b. The leeward side distribution tank part 22 which distributes a refrigerant | coolant to the side tube 21c is provided. The refrigerant evaporator 1 is provided at the downstream end of the plurality of leeward tubes 21c constituting the first core portion 21a, and collects the refrigerant that has passed through the leeward tubes 21c; A second collecting portion 23b that is provided at the downstream end of the plurality of leeward tubes 21c constituting the core portion 21b and collects the refrigerant that has passed through the leeward tube 21c, and a plurality of upwind portions constituting the third core portion 11a. Provided at the upstream end of the tube 11c, and provided at the upstream ends of the first distributor 13a for distributing the refrigerant to the windward tube 11c and the plurality of windward tubes 11c constituting the fourth core part 11b, And a second distributor 13b that distributes the refrigerant to the tube 11c. Further, the refrigerant evaporator 1 includes a first passage 33a that communicates the first collection portion 23a and the second distribution portion 13b, a second passage 33b that communicates the second collection portion 23b and the first distribution portion 13a, It has.

  As described above, in the configuration in which the refrigerant flows into the leeward distribution tank unit 22 from the refrigerant inlet 22a in the vicinity of the first core unit 21a, the refrigerant distributed to the first core unit 21a and the second core unit 21b Differences in flow rate occur. However, in the above configuration, by replacing the refrigerant so as to intersect, the flow rate of the refrigerant in which a part of the air passing through the first core portion 21a and the third core portion 11a exchanges heat, the second core portion 21b, It becomes possible to reduce the difference between the flow rate of the refrigerant that exchanges heat with the other part of the air that passes through the fourth core portion 11b. As a result, it is possible to suppress an uneven temperature distribution in the air passing in the X direction.

  As a result, while the compressor is being driven, it is possible to suppress a deviation in the amount of cold heat stored in the cool storage material 41 in the plurality of cool storage cases 40. As a result, while the compressor is stopped, it is possible to continue air cooling while suppressing the uneven temperature distribution by the cold storage material 41.

  The embodiments of the present invention have been described above with reference to specific examples. However, the present invention is not limited to these specific examples. In other words, those specific examples that have been appropriately modified by those skilled in the art are also included in the scope of the present invention as long as they have the characteristics of the present invention. Each element provided in each of the specific examples described above and its arrangement, material, condition, shape, size, and the like are not limited to those illustrated, but can be changed as appropriate.

1: Refrigerant evaporator 11: Windward core portion 11a: Third core portion 11b: Fourth core portion 11c: Windward tube 13a: First distribution portion 13b: Second distribution portion 21: Downstream core portion 21a: First Core portion 21b: second core portion 21c: leeward side tube 22: leeward side distribution tank portion 22a: refrigerant inlet 23a: first collecting portion 23b: second collecting portion 40: cool storage case 41: cool storage material

Claims (3)

A refrigerant evaporator (1) that exchanges heat between a fluid to be cooled and a refrigerant,
An upwind core section (11) having a plurality of upwind tubes (11c) arranged with a gap between each other, and performing heat exchange between the refrigerant flowing through the plurality of upwind tubes and the fluid to be cooled;
A plurality of leeward side tubes (21c) arranged at a distance from each other, and arranged to overlap the windward side core part on the downstream side of the windward side core part in the flow direction of the fluid to be cooled; A leeward core portion (21) for exchanging heat between the refrigerant flowing in the leeward tube and the cooled fluid that has passed through the leeward core portion;
A communication channel (13, 23, 33) for guiding the refrigerant flowing out from the downstream end of the leeward tube to flow into the upstream end of the leeward tube;
The cold storage material (41) is accommodated therein, and is disposed in a gap between the adjacent windward tubes and a gap between the adjacent leeward tubes, and the windward core part and the leeward core part. A plurality of cold storage cases (40) arranged so as to straddle the
Wherein the windward tube, a gas-liquid mixed region and the refrigerant in the refrigerant and the vapor phase of a liquid phase you mixed with (GL), Luz Pahito zone refrigerant is heated in the vapor phase and (SH), are formed,
When the boundary between the gas-liquid mixture area and the superheat area is a superheat boundary (SH1),
The cold storage case is disposed adjacent to the windward tube so as to face the gas-liquid mixed area and the superheat area,
The said refrigerant | coolant storage material is a refrigerant evaporator accommodated only in the site | part arrange | positioned in the said gas-liquid mixture area side rather than the said superheat boundary among the said cold storage case. The windward core portion and the leeward core portion are disposed so as to be plane-symmetric with respect to a predetermined plane orthogonal to the flow direction of the fluid to be cooled.
The plurality of cool storage cases are symmetrical with respect to planes passing through the centers of the windward core portion and the leeward core portion in a direction in which the plurality of windward tubes and the plurality of leeward tubes are arranged. The refrigerant evaporator according to claim 1, wherein the refrigerant evaporator is disposed at a position. The leeward core portion is
A first core portion (21a) that exchanges heat between a part of the fluid to be cooled and a part of the refrigerant;
A second core portion (21b) that performs heat exchange between the other part of the fluid to be cooled and the other part of the refrigerant,
The windward core portion is
A third core portion (11a) which is arranged so as to overlap the first core portion in the flow direction of the fluid to be cooled and allows heat exchange between a part of the fluid to be cooled and another portion of the refrigerant. When,
A fourth core portion (11b) that is arranged so as to overlap with the second core portion in the flow direction of the fluid to be cooled and allows heat exchange between another portion of the fluid to be cooled and a portion of the refrigerant. And having
A refrigerant inlet (22a) is provided in the vicinity of the first core portion, and is provided at the upstream ends of a plurality of leeward tubes constituting the first core portion and the second core portion, and the leeward tube has a refrigerant A distribution tank section (22) for distributing
A first collecting portion (23a) that is provided at a downstream end of the plurality of leeward tubes constituting the first core portion and collects the refrigerant that has passed through the leeward tubes;
A second collecting portion (23b) that is provided at a downstream end of the plurality of leeward tubes constituting the second core portion and collects the refrigerant that has passed through the leeward tubes;
A first distributor (13a) that is provided at an upstream end of a plurality of windward tubes constituting the third core portion and distributes the refrigerant to the windward tubes;
A second distribution part (13b) provided at the upstream end of the plurality of windward tubes constituting the fourth core part and distributing the refrigerant to the windward tubes;
A first passage (33a) communicating the first collecting portion and the second distribution portion;
The refrigerant evaporator according to claim 1 or 2, further comprising a second passage (33b) communicating the second collecting portion and the first distribution portion.

Images