JP2017040389A - Heat exchanger of heat pump application apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchange device of a new heat pump application apparatus capable of unifying a temperature distribution of a refrigerant flowing in upper and lower regions of a heat exchanger including a plurality of refrigerant tubes arranged in a manner that they are stacked on heat exchange fins extended in a vertical direction and allow the refrigerant to independently flow.SOLUTION: In a heat exchanger including a plurality of refrigerant tubes 3 which are stacked at intervals while penetrating through heat exchange fins 2 extended in a vertical direction, and in which a refrigerant independently flows, wind velocity control plates 36U, 36B implementing control to unify a wind velocity in a vertical direction, of outside air flowing into the heat exchanger, are disposed at upper and lower regions of the heat exchanger of a space between an outside air outlet side of the heat exchanger 104 and a blower fan 107. As the wind velocity distribution of the outside air flowing into the heat exchanger can be corrected to a direction to be unified, the temperature distribution of the refrigerant in the heat exchanger can be maximally unified.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a heat exchange device used for heat pump application equipment such as a heat pump type hot water supply device and a heat pump type air conditioner, and more particularly to a heat exchange device for a heat pump application equipment including a blower fan and a heat exchanger through which a refrigerant flows. It is.

  In heat pump applied equipment such as a heat pump type hot water supply apparatus and a heat pump type air conditioner based on the refrigeration cycle, a heat exchange apparatus that exchanges heat between refrigerant and outside air is used. This heat exchange device evaporates or condenses the refrigerant by exchanging heat between the outside air (air) sucked by a blower fan such as a propeller fan and the refrigerant flowing through the heat exchanger.

  For example, Japanese Patent Laying-Open No. 2014-224737 (Patent Document 1) discloses a heat exchange device (evaporator) used in a heat pump hot water supply device. In this heat exchange device, heat exchange fins are arranged along the up-and-down direction (top and bottom direction), and a refrigerant pipe penetrates and is arranged so as to be orthogonal to the heat exchange fins. That is, the refrigerant pipe is disposed substantially parallel to the installation surface (ground).

  The evaporator of Patent Document 1 is of a cross fin tube type, and includes heat exchange fins that are heat transfer surfaces on the outside air side and a plurality of refrigerant tube groups. Specifically, the heat exchange fins are composed of a plurality of plate-like fins extending in the vertical direction, and are arranged so that the plate surfaces of the fins face each other with a predetermined gap. The outside air flows between the plate surfaces of the heat exchange fins to exchange heat.

  The refrigerant pipe penetrates so as to be substantially orthogonal to each fin of the heat exchange fin, and is fixed to each fin. Specifically, the refrigerant pipe penetrates so as to be substantially orthogonal to each fin of the heat exchange fin, and then turns back and penetrates again so as to be substantially orthogonal to each fin of the heat exchange fin. That is, the plurality of refrigerant tubes penetrating the heat exchange fins are arranged so that the length direction of the refrigerant tubes is aligned in a direction perpendicular to the external airflow.

  And the refrigerant | coolant pipe | tube is arrange | positioned so that it may mutually laminate | stack at intervals in the up-down direction of a heat exchange fin, respectively, and the some refrigerant | coolant tube group is formed. In other words, the evaporator of Patent Document 1 includes a distribution pipe and a junction pipe, and the refrigerant pipe is divided into six parts between the distribution pipe and the junction pipe, and each refrigerant pipe is independent of the refrigerant. Is flowing. In other words, the uppermost refrigerant pipe is diverted from the distribution pipe and exchanged with the outside air through the heat exchange fins, and then merged in the merge pipe. The lower refrigerant pipe is also diverted from the distribution pipe and passed through the heat exchange fins. After the heat exchange with the outside air, it is joined at the junction pipe. Therefore, the refrigerant flowing through both refrigerant tubes flows without being mixed while exchanging heat with the heat exchange fins. The remaining refrigerant tubes have the same configuration.

JP 2014-224737 A

  In such a heat exchange device, the heat exchange efficiency between the refrigerant flowing through the heat exchanger and the outside air is important, and this heat exchange efficiency is greatly influenced by the wind speed distribution of the outside air passing through the heat exchanger. In the case where the wind speed distribution, which is the flow rate of outside air when flowing into the heat exchanger, is not uniform with respect to the heat exchanger, the air volume of the entire heat exchanger depends on the ventilation resistance of the portion where the wind speed is high. For this reason, when the wind speed distribution is not uniform, there is a phenomenon in which the air volume is reduced and the coefficient of performance (COP) is lowered as compared with the case where the wind speed distribution is substantially uniform.

  Usually, the external shape of the heat exchanger is formed in a laterally long rectangular parallelepiped (some cases are L-shaped bent from the end face of the rectangular parallelepiped), and the blower fan facing the heat exchanger of the rectangular parallelepiped Are arranged so as to face each other near the center of the rectangular parallelepiped. And the structure with which the heat exchanger and the ventilation fan are accommodated in the external housing | casing is common. For this reason, the outside air flowing into the heat exchanger has a strong tendency to enter toward the blower fan, and the wind speed is slow in the vertical region on the vertical end face side and the left and right region on the horizontal end face side of the heat exchanger. The phenomenon that occurs.

  And, as shown in Patent Document 1, in the heat exchanger in which the refrigerant pipes are arranged so as to be separated and independent in the vertical direction, when a wind speed distribution with a slow wind speed is generated in the vertical direction, Since the wind speed of the outside air flowing through the upper and lower regions is slow, the heat exchange efficiency of the refrigerant pipes arranged in the upper and lower regions is lowered. Even if the wind speed of the outside air is slow in the left and right regions, the refrigerant pipe extends in the left-right direction, so that the refrigerant crosses near the center of the heat exchanger where the wind speed is fast from the left and right, and the refrigerant exchanges heat near this center. Therefore, the influence of the decrease in the wind speed in the left and right regions is not so great.

  In this way, in the refrigerant pipes arranged independently to be stacked in the vertical direction of the heat exchanger, the refrigerant in the refrigerant pipes arranged in the upper and lower regions where the wind speed is slow is difficult to exchange heat, and the central region where the wind speed is fast The refrigerant in the refrigerant pipe arranged in the heat exchanger is easily heat exchanged. For this reason, the refrigerant temperature is unevenly distributed in the vertical direction of the heat exchanger, and there is a problem that the heat exchange performance cannot be improved. Therefore, it is only necessary to increase the wind speed in the upper and lower regions of the heat exchanger so that the vertical wind speed distribution of the outside air flowing into the heat exchanger approaches the uniform wind speed distribution. As a result, the coefficient of performance (COP) can be improved.

  An object of the present invention is to increase the wind speed of the outside air flowing in the upper and lower regions of a heat exchanger having a plurality of refrigerant tube groups that are stacked at intervals on heat exchange fins extending in the vertical direction and in which refrigerant flows independently. An object of the present invention is to provide a heat exchange device for a new heat pump device capable of correcting the wind speed distribution so as to approach the uniform wind speed distribution.

  A feature of the present invention is that the heat exchanger includes a plurality of refrigerant tubes that are stacked at intervals through the heat exchange fins extending in the vertical direction, and in which the refrigerant flows independently. Control so that the wind speed of one or both of the up and down directions of the outside air flowing into the heat exchanger is made uniform in at least one or both of the upper and lower regions of the heat exchanger in the space between the blower fans There is a wind speed control board in place.

  According to the present invention, since it is possible to correct the wind speed distribution of the outside air flowing in the vertical direction of the heat exchanger in a direction to make it uniform, a plurality of refrigerant tubes arranged so that the refrigerant flows independently in the vertical direction are provided. The temperature distribution of the refrigerant in the heat exchanger provided can be made uniform. As a result, the coefficient of performance (COP) can be improved.

  Here, the homogenization is not strictly uniform, and means that it can be made uniform as compared with the case where no wind speed control plate is provided.

It is a block diagram which shows the structure of the heat pump type water heater to which this invention is applied. It is an external appearance perspective view of the heat exchanger used for the heat exchange apparatus shown in FIG. It is a sectional side view of the heat exchange apparatus which becomes the 1st Embodiment of this invention. It is an external appearance perspective view which shows the arrangement configuration of the wind speed control board and heat exchanger which are shown by FIG. It is a sectional side view of the heat exchange apparatus for demonstrating the effect | action of this embodiment. It is a graph for comparing the temperature distribution of the refrigerant | coolant of the conventional heat exchanger and the heat exchanger of this embodiment. It is a sectional side view of the heat exchange apparatus which becomes the 2nd Embodiment of this invention. It is a sectional side view of the heat exchange apparatus which becomes the 3rd Embodiment of this invention. It is a sectional side view of the heat exchange apparatus which becomes the 4th Embodiment of this invention. It is a block diagram which shows the structure of the heat pump type air conditioning apparatus which becomes the 5th Embodiment of this invention. It is a sectional side view of the conventional heat exchange apparatus. It is a graph which shows the temperature distribution of the refrigerant | coolant of the conventional heat exchanger.

  Next, embodiments of the present invention will be described in detail with reference to the drawings. However, the present invention is not limited to the following embodiments, and various modifications and application examples are included in the technical concept of the present invention. Is included in the range.

  First, before describing an embodiment of the present invention, a schematic configuration of a heat pump water heater to which the present invention is applied will be described. Moreover, in order to help an understanding of the present invention, the configuration of a conventional heat exchange device and its problems will also be described.

  FIG. 1 shows an outline of a CO2 heat pump water heater system. The heat pump water heater includes a heat pump unit 50 equipped with a heat pump cycle 100 that heats cold water during boiling operation and boils it into hot water, a water-side cycle 200 that operates during boiling operation, and a hot water supply channel group that operates during hot water supply. The hot water storage unit 60 is mounted.

  The heat pump cycle 100 has a configuration in which each element of the compressor 101, the water / refrigerant heat exchanger 102, the expansion valve 103, and the evaporator 104 is connected in an annular shape, and the evaporator 104 is blown as a blowing means for flowing outside air. A fan 107 is provided. Here, a configuration including the evaporator 104 and the blower fan 107 is a heat exchange device, and the evaporator 104 is a heat exchanger.

  The water-side cycle 200 has a configuration in which a hot water storage vessel 201, a circulating pump for boiling 202, and a water / refrigerant heat exchanger 102 are connected in an annular shape. The hot water supply flow path group includes a flow path in which a water pipe 204, a hot water storage container 201, and a hot water supply port 203 are connected in series, and a flow path 205 in which the water pipe 204 and the inlet of the hot water supply port 203 are directly connected.

  The heat pump cycle 100 contains R744, which is a CO2 refrigerant, but the refrigerant is not limited to R744, and various refrigerants such as R32 and R410A can be selected.

  FIG. 2 schematically shows the evaporator 104 which is a heat exchanger. The evaporator 104 has a heat exchange fin 2 that forms a heat transfer surface with the outside air, and a cross fin tube type configuration in which the refrigerant pipe 3 is orthogonal to the heat exchange fin 2. The heat exchange fin 2 extends in the vertical direction (vertical direction), and the refrigerant pipe 3 is fixed so as to penetrate the heat exchange fin 2 so as to be orthogonal to the heat exchange fin 2. Therefore, the refrigerant pipe 3 is arranged substantially parallel to the installation surface.

  The refrigerant flow path is mainly composed of a distribution unit 10, an evaporator inlet flow channel 11, a refrigerant heat transfer unit 12, an evaporator outlet flow channel 13, and a merging unit 14, and the distribution unit 10 has one to six refrigerant flow channels. After branching through and passing through the refrigerant heat transfer section 12, the merge section 14 integrates again into one flow path.

  Here, the refrigerant channel inlet 1A is connected to the refrigerant channel outlet 1B. Similarly, the refrigerant channel inlet 2A is the refrigerant channel outlet 2B, the refrigerant channel inlet 3A is the refrigerant channel outlet 3B, and the refrigerant channel inlet. 4A is connected to the refrigerant channel outlet 4B, the refrigerant channel inlet 5A is connected to the refrigerant channel outlet 5B, and the refrigerant channel inlet 6A is connected to the refrigerant channel outlet 6B. In FIG. 2, a six-branch configuration is assumed, but it is sufficient if there are at least two or more branches.

  And the refrigerant | coolant pipe | tube is arrange | positioned so that it may mutually laminate in the up-down direction of the heat exchange fin 2 at intervals, and the some refrigerant | coolant tube group is formed. That is, the distribution unit 10 and the junction unit 14 are provided, and the refrigerant pipe 3 is divided into six parts between the distribution unit 10 and the junction unit 14, and the refrigerant flows through each refrigerant pipe 3 independently. It is.

  As can be seen from FIG. 2, the uppermost refrigerant pipe 3 is diverted from the distributor 10, passes through the heat exchange fins 2 from the refrigerant flow path inlet 1 </ b> A, and is merged at the merge section 14 from the refrigerant flow path outlet 1 </ b> B. The refrigerant pipe 3 below is also diverted from the distribution unit 10, passes through the heat exchange fins 2 from the refrigerant flow path inlet 2 </ b> A, and is merged at the merge section 14 from the refrigerant flow path outlet 2 </ b> B. Similarly, the remaining refrigerant pipes have the same configuration. Therefore, the refrigerant flowing through each refrigerant pipe 3 flows independently without being mixed while exchanging heat with the heat exchange fins 2.

  The refrigerant flow path is configured to go to the outlet while reciprocating between the front side and the back side according to the broken line in FIG. 2, and the positional relationship of the six flow paths after branching is not changed in the vertical direction. It is the structure which is laminated | stacked and arranged in a line.

  Next, operation | movement of the hot-water supply system mentioned above is demonstrated easily using FIG. After the refrigerant is compressed by the compressor 101 to be in a high temperature and high pressure state, the water / refrigerant heat exchanger 102 heats the cold water sent from the lower part of the hot water storage vessel 201 by the circulating pump 202 for boiling, Instead, it radiates its own heat and performs heat exchange.

  Then, the refrigerant passes through the expansion valve 103 to become a low temperature and low pressure state, and then receives heat from the outside air sent by the blower fan 107 in the evaporator 104 and then flows into the compressor 101 again. . In the water / refrigerant heat exchanger 102, the water and the refrigerant flow in opposite directions, and the hot water heated by the refrigerant and having a high temperature is returned to the upper part of the hot water storage container 201.

  At the time of hot water supply, hot water flows from the upper part of the hot water storage container 201 to the hot water supply port 203, and at the same time, tap water is supplied from the water pipe 204 to the hot water supply port 203. Hot water and tap water are mixed at the inlet of the hot water outlet 203 and then flow out of the hot water outlet 203.

  Next, the operation of the evaporator 104 will be described. When the heat pump cycle 100 is driven, the blower fan 107 rotates, so that a flow of outside air from the evaporator 104 to the blower fan 107 is generated in the air passage space 30. At the same time, as shown in FIG. 2, the refrigerant that has flowed into the evaporator 104 is branched into six flow paths by the distribution unit 10, and then passes through the evaporator inlet flow path 11 to the refrigerant heat transfer unit 12. And flows through the respective flow paths and absorbs heat from the outside air, and then merges at the merge section 14 via the evaporator outlet flow path 13.

  The refrigerant flows in from the end of the evaporator 104, passes through the evaporator 104 in a substantially horizontal direction and reaches the end on the opposite side, and then circulates back to the adjacent stage while returning to the outside air. Get heat from. There are other types of evaporators, such as an evaporator that flows in from the end of the evaporator 104 and flows out from the end on the opposite side without turning back, but this can be used.

  Next, the structure and operation of a conventional heat exchange device in such a heat pump type hot water heater will be described. FIG. 11 shows a side view of a conventional heat exchange device.

  The heat exchange device 40 includes an evaporator 104 and a blower fan 107 inside, and an air passage space 30 is formed between the evaporator 104 and the blower fan 107. The blower fan 107 is fixed to the mounting bracket 35 by a fixing means such as a bolt. As the blower fan 107 rotates, outside air outside passes through the evaporator 104 and flows into the air passage space 30, and is then discharged from the blower fan 107 to the outside again. Therefore, when the outside air passes through the evaporator 104, heat exchange is performed between the refrigerant and the outside air via the heat exchange fins 2.

  And the wind speed distribution of the entrance of the evaporator 104 of the up-down direction when the external air from the outside flows into the evaporator 104 is described on the right side of FIG. Here, the inlet region shared by the six refrigerant pipes 3 extending from the refrigerant flow path inlets 1 </ b> A to 6 </ b> A is divided into the flow paths 1 to 6 corresponding to the respective refrigerant pipes 3.

  In the conventional heat exchange apparatus, the wind speed in the vertical direction at the inlet of the evaporator 104 has a wind speed distribution having a region where the wind speed is slow in the vertical region, as shown in FIG. For this reason, since the refrigerant | coolant of the flow path 3 and the flow path 4 which passes the central part vicinity of the evaporator 104 receives many airflows (outside air), heat exchange is accelerated | stimulated and it is easy to evaporate. On the other hand, the refrigerant in the flow channel 1 and the flow channel 6 (including the flow channel 2 and the flow channel 5 in some cases) located in the upper and lower regions of the evaporator 104 has a small air volume, and therefore heat exchange is suppressed and it is difficult to evaporate. There is a tendency.

  In addition, as a cause of the region where the wind speed is slow in the vertical direction, the installation position of the blower fan 107, the asymmetry of the vertical direction of the air passage shape, and the like can be considered. This is because the vertical dimension of the evaporator 104 is set large. For this reason, the suction pressure in the upper and lower regions is higher than that in the vicinity of the rotation center of the blower fan 107, and it is considered that the wind speed is thereby lowered. As a result, the wind speed distribution as shown on the right side of FIG. 11 is obtained.

  FIG. 12 shows the temperature distribution of the refrigerant near the outlet of the evaporator 104 with respect to the wind speed distribution shown in FIG. The horizontal axis of FIG. 12 is the number of the refrigerant flow path after branching in the distribution unit 10, and the vertical axis is the refrigerant temperature. As shown in FIG. 12, the refrigerant temperature of the flow path 3 and the flow path 4 passing through the area with a large air volume is high, while the refrigerant temperature of the flow path 1 and the flow path 6 passing through the area with a small air volume is low. Recognize. This means that the heat transfer surfaces of the gas refrigerant having a low heat transfer coefficient are increased in the flow path 3 and the flow path 4, and the heat transfer of the entire evaporator is higher than that in the case where the entire temperature becomes equal. As a result, the evaporation pressure decreases, that is, the coefficient of performance (COP) of the heat pump cycle 100 decreases.

  The present invention proposes a heat exchanging apparatus capable of improving the coefficient of performance (COP) of the heat pump cycle by suppressing the occurrence of such a region where the wind speed is low in the vertical direction of the heat exchanger.

  Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the drawings. The same reference numerals as those in FIGS. 1, 2, and 11 are the same components or components having equivalent functions.

  In FIG. 3, as in FIG. 11, the heat exchanging device 40 includes a blower fan 107 fixed inside the evaporator 104 and the mounting bracket 35, and a predetermined length between the evaporator 104 and the blower fan 107. The air passage space 30 is formed. Here, the difference from the conventional heat exchange device is that wind speed control plates 36U and 36B inclined at a predetermined angle in the flow direction of the outside air are arranged in the upper and lower regions of the air passage space 30.

  The wind speed control plates 36U and 36B are formed in a plate-like rectangular shape, and both ends of the plate-like rectangle are fixed to the mounting bracket 35. Therefore, outside air can flow freely except for the fixed portions at both ends of the plate-like rectangle. The present embodiment is characterized in that at least the wind speed of the flow path 1 and the flow path 6 is increased by the wind speed control plates 36U and 36B. The functions and functions of the wind speed control plates 36U and 36B will be described later. The wind speed control plates 36U and 36B can be made of metal or synthetic resin, and are made of synthetic resin in this embodiment.

  Then, when the blower fan 107 rotates, the outside air outside passes through the evaporator 104 and flows into the air passage space 30, and is then discharged from the blower fan 107 to the outside again. Therefore, when the outside air passes through the evaporator 104, heat exchange is performed between the refrigerant and the outside air via the heat exchange fins 2. Then, the wind speed distribution at the inlet when the outside air outside flows into the evaporator 104 is shown on the right side of FIG. Here, similarly to FIG. 11, the inlet region shared by the refrigerant flow path inlets 1 </ b> A to 6 </ b> A is divided into flow paths 1 to 6 corresponding to the respective refrigerant flow path inlets 1 </ b> A to 6 </ b> A.

  In this embodiment, as shown in FIGS. 3 and 4, the upper wind speed control plate 36 </ b> U and the lower wind speed control plate 36 </ b> B are evaporated in the air passage space 30 between the blower fan 107 and the evaporator 104. It is provided in the upper region and the lower region of the vessel 104. Here, in the present embodiment, the upper region is a region where the flow channels 1 and 2 exist in the vertical direction of the heat exchanger 104, and the lower region is the flow channel in the vertical direction of the heat exchanger 104. This is an area where 6 to 5 exist.

  The upper wind speed control plate 36U and the lower wind speed control plate 36B extend along the inner side surface of the evaporator 104 perpendicular to the vertical direction in parallel with the inner side surface of the evaporator 104 as shown in FIG. It is formed in a flat shape. Therefore, the upper wind speed control plate 36 </ b> U and the lower wind speed control plate 36 </ b> B have a flat plate shape having long sides in the penetration direction of the refrigerant pipe 3. The length of the long side is not less than the diameter of the blower fan 107 and is determined between 70% and 90% of the lateral length of the outlet face of the heat exchanger facing the blower fan 107. As a result, the wind speed of the outside air can be increased over substantially the lateral length of the heat exchanger.

  Further, the arrangement positions of the upper wind speed control plate 36U provided in the upper area and the lower wind speed control board 36B provided in the lower area are arranged so as to be accommodated in the flow path 1 and the flow path 6 as shown in FIG. However, it may be changed depending on the arrangement position of the blower fan 107. For example, when the blower plate 107 is biased to one side in the vertical direction, the positions and shapes of the wind speed control plates 36U and 36B are corrected along this.

  Further, the wind speed control plates 36U and 36B are fixed so that the short sides of the wind speed control plates 36U and 36B are inclined at a predetermined angle in the flow direction of the outside air flowing through the air passage space 30. This inclination is set so that the rear end edges of the short sides of the wind speed control plates 36U and 36B are directed to the vicinity of the center in the vertical direction of the heat exchanger 104 and are along the flow direction of the outside air. In other words, in the air passage space 30, the upper air passage formed by the wind speed control plate 36U and the external housing and the lower air passage formed by the wind speed control plate 36B and the external housing are arranged along the flow direction of the outside air. The cross-sectional area continuously increases, and the central air passage sandwiched between the upper wind speed control plate 36U and the lower wind speed control plate 36B decreases continuously along the flow direction of the outside air. It has become.

  As a result, the wind speed control plates 36U and 36B have a function of controlling the flow of outside air flowing out from the evaporator 104. This flow control action makes the wind speed distribution on the inlet side of the evaporator 104 more uniform. It is corrected so that

  The present embodiment is directed to a heat exchanger having a wind speed distribution in which the wind speed near the center of the evaporator 104 as shown in FIG. 11 is high and the wind speed in the upper region and the lower region is low, and this wind speed distribution is improved. For this purpose, the upper wind speed control plate 36U and the lower wind speed control plate 36B are arranged in the upper and lower regions in the vertical direction on the outlet side of the evaporator 104.

  The wind speed distribution indicated by a broken line on the right side of FIG. 3 is obtained by plotting, in the vertical direction, values obtained by averaging the entire wind speed flowing into the conventional evaporator 104 in the refrigerant flow direction. Moreover, the average value of the wind speed distribution in the vertical direction is indicated by a one-dot chain line.

  In the present embodiment, the rear edge of each of the wind speed control plates 36U and 36B (the end surface on the most downstream side as viewed from the flow of outside air) is the wind speed distribution shown on the right side of FIG. The wind speed control plates 36U and 36B are arranged in the wind path space 30 so as to be located in the portion where the wind speed is generated near the intersection of the wind speed distribution lines when the wind speed control plates 36U and 36B are not provided.

  Therefore, the outside air flowing out from the evaporator 104 is a central wind between the upper wind path 31 above the rear end edge of the upper wind speed control plate 36U and the rear end edges of the upper wind speed control plate 36U and the lower wind speed control plate 36B. It flows out through the three air passages of the passage 32 and the lower air passage 33 below the rear end edge of the lower air speed control plate 36B.

  In this figure, the upper wind path 31, the central wind path 32, and the lower wind path 33 are defined with reference to the rear edges of the upper wind speed control plate 36U and the lower wind speed control plate 36B. The upper air passage 31, the central air passage 32, and the lower air passage 33 may be defined with reference to the leading edges of the plate 36U and the lower air speed control plate 36B.

As for the above-described three air paths divided by the air speed control plates 36U and 36B, the average air speed of the upper air path 31 is U _1AVE and the average air speed of the lower air path 33 is shown on the right side of FIG. the _{U 2AVE,} if the average wind speed for the entire set to _{U AVE,} the inlet of the flow path cross-sectional area _{a 1IN} the upper air passage 31 formed by the upper air velocity control plate 36U, the relationship between the flow path cross-sectional area _{a 1EX} the outlet It is expressed by the following equation (1).

Further, the relationship between the lower flow path cross-sectional area A _2IN of the lower air passage 33 formed by the lower wind speed control plate 36B and the flow path cross-sectional area A _2EX of the outlet side is expressed by the following equation (2). .

  And the wind speed distribution by this embodiment is shown on the right side of FIG. 5, the wind speed distribution before improvement is shown with a broken line, and the wind speed distribution after improvement is shown with the continuous line. Here, before improvement is the heat exchange apparatus shown in FIG. 11, and after improvement is the heat exchange apparatus according to the present embodiment shown in FIG. In the heat exchange apparatus according to the present embodiment, the wind speed distribution is corrected by the wind speed control plates 36U and 36B so that the wind speed distribution at the inlet of the evaporator 104 approaches uniformly.

More specifically, the average wind speed of the upper air passage 31 on the suction surface AA of the blower fan 107 is U _1AVE , the average average air speed of the evaporator 104 is U _AVE , and the inlet cross-sectional area of the upper air passage 31 is A _1IN. , if the outlet cross-sectional area was a _1EX, the continuity equation relating doorway of the upper air passage 31, the inlet average wind speed U _1IN the upper air passage 31 from the equation (1), the following equation (3) is satisfied .

Similarly, the average wind speed of the lower air _passage 33 on the suction surface AA of the blower fan 107 is U _2AVE , the average average air speed of the evaporator 104 is U _AVE , and the inlet cross-sectional area of the lower air _passage 33 is A _2IN , When the exit cross-sectional area is A _2EX , the following equation (4) is established for the inlet average wind speed U _2IN of the lower air passage 33 from the continuous equation relating to the inlet / outlet of the lower air passage 33 and the equation (2). .

  The above-described relationship is that the wind speed control plates 36U and 36B increase the inlet wind speed of the evaporator 104 corresponding to the upper air path 31 and the lower air path 33 so as to be close to the average wind speed. This means that the average wind speed is reduced and this improves the overall wind speed distribution in a uniform direction.

  FIG. 6 shows the refrigerant temperature distribution at the outlet of the evaporator 104 when the refrigerant is evaporated in the improved heat exchange apparatus shown in FIG. In FIG. 6, a solid line is the heat exchange apparatus shown in FIG. 3, and a broken line is the heat exchange apparatus shown in FIG. As shown in FIG. 6, the refrigerant temperature at the outlet of the evaporator 104 decreases due to a decrease in the amount of air exchanged with the refrigerant in the flow paths 3 and 4, while the flow located in the vertical region of the evaporator 104. It can be seen that since the air volume in the passage 1 and the passage 6 has increased, the refrigerant temperature has risen, and the temperature distribution of the refrigerant at the outlet of the evaporator 104 has been corrected in a uniform direction.

  As a result, the proportion of the gas refrigerant in the entire evaporator 104 decreases, and it becomes possible to improve the evaporation pressure and improve the coefficient of performance (COP) by improving the heat transfer coefficient of the refrigerant flow path.

  The basic idea of the present embodiment is to improve the nonuniformity of the wind speed distribution by the theory of the continuous equation, and the frictional resistance of the wind speed control plates 36U and 36B is dominant as the fluid resistance. Although the total air volume flowing through the evaporator 104 is reduced by the generation of the frictional resistance, the effect of improving the performance by improving the temperature distribution at the refrigerant outlet is superior by the small pressure resistance.

  From the above, this method has a technical difference that the effect of improving the performance is large because the pressure resistance is significantly smaller than the method of forcing the flow resistance in the high wind speed region by pressure resistance. I understand.

  Here, in the present embodiment, the inclination of the upper wind speed control plate 36U and the lower wind speed control plate 36B is determined based on the average wind speed of each region partitioned by the wind speed control plates 36U, 36B. The same effect can be obtained even when the local wind speed of the part is used.

  Moreover, since the length of the long side direction of the wind speed control plates 36U and 36B is limited to a region where the refrigerant heat transfer section 12 is present, it may be short. In the relationship between the formulas (1) and (2), the wind speed It is assumed that the effect of making the distribution uniform is insufficient.

  In this case, the inclination of the wind speed control plates 36U and 36B may be set to be large (the cross-sectional area on the inlet side is reduced or the cross-sectional area on the outlet side is increased). What is necessary is just to make the relationship of an expression materialize. In addition, although the following formula | equation is an average wind speed, you may use a local wind speed.

  Similarly, for the lower air passage 33, the following relationship (6) may be satisfied.

  In this way, even when the lengths of the wind speed control plates 36U and 36B in the long side direction are shortened, the effect of uniforming the wind speed distribution can be obtained.

  In the embodiment shown in FIG. 3, the ratio of the length in the vertical direction of the upstream air passage 31, the central air passage 32, and the lower air passage 33 is approximately 1/6, 4/6, 1/6. The air speed control plates 36U and 36B are provided in the length range of the upstream air passage 31 and the lower air passage 33. However, the vertical length of each air passage may be set with a margin, and the ratio of the vertical lengths of the upstream air passage 31, the central air passage 32, and the lower air passage 33 is 1 / The ratio can be changed to 3, 1/3 and 1/3. Therefore, it is sufficient that the wind speed control plates 36U and 36B are disposed within this range. In other words, the height direction positions of the upstream air passage 31 and the lower air passage 33 correspond to the above-described upper region and lower region.

  In the embodiment described above, a cross fin tube type is used as the evaporator 104. However, in the heat exchange device of this embodiment, a flat tube composed of a plurality of fine flow channels is laminated in the vertical direction. In addition, the present invention is also applicable to a refrigerant whose heat transfer surface is planar, such as a parallel flow type heat exchanger arranged in parallel.

  As described above, according to the present embodiment, in the heat exchanger provided with a plurality of refrigerant tubes that are stacked at intervals through the heat exchange fins extending in the vertical direction and the refrigerant flows independently, A wind speed control plate for controlling the wind speed in the vertical direction of the outside air flowing into the heat exchanger to be uniform is arranged in the upper and lower regions of the heat exchanger in the space between the outlet side of the heat exchanger and the blower fan.

  According to this, since it is possible to correct the wind speed distribution of the outside air flowing into the heat exchanger in a direction to make it uniform, the temperature distribution of the refrigerant in the heat exchanger can be made as uniform as possible. Therefore, the proportion of the gas refrigerant in the entire evaporator 104 is reduced, and it is possible to improve the evaporation pressure and improve the coefficient of performance (COP) by improving the heat transfer coefficient of the refrigerant flow path.

  Next, a second embodiment of the present invention is shown in FIG. The second embodiment is different from the first embodiment in that the upper wind speed control plate 36U is omitted. In this case, the improvement effect of the wind speed distribution is smaller than that of the first embodiment, and the coefficient of performance (COP) is also lowered, but the following actions and effects are newly obtained. On the right side, the wind speed distribution of this embodiment is shown for reference.

  In the frosting condition where frost and ice adhere to the heat exchange fins 2 of the evaporator 104, more outside air flows in the lower region of the evaporator 104 than in the first embodiment, so that the growth rate of frost and ice can be suppressed. effective. In particular, since ice tends to be generated on the lower side due to gravity, the effect of suppressing the growth rate of frost and ice is greater than the arrangement of only the upper wind speed control plate 36U. Further, since the upper wind speed control plate 36U is omitted, it is possible to reduce the material cost.

  Next, a third embodiment of the present invention is shown in FIG. The third embodiment differs from the first embodiment in the cross-sectional shape perpendicular to the direction in which the outside air flows on the wind speed control plates 36U and 36B, and the surface shape on the surface side where the air path expands along the outside air flow. Is arcuate. On the right side, the wind speed distribution of this embodiment is shown for reference.

  In this case, since the occurrence of separation due to the expansion of the air path can be suppressed by the Coanda effect in which the outside air tends to flow along the surfaces of the wind speed control plates 36U and 36B, the inclination angle of the wind speed control plates 36U and 36B compared to the flat plate Even when the pressure is increased, generation of pressure resistance can be suppressed. As a result, it is possible to dispose the wind speed control plates 36U and 36B having a larger inclination than that of the first embodiment.

  Next, FIG. 9 shows a fourth embodiment of the present invention. The fourth embodiment differs from the first embodiment in the cross-sectional shape of the wind speed control plates 336U and 36B perpendicular to the direction in which the outside air flows, and the leading edge is round and the trailing edge is sharp along the outside air flow. It is different in that it has a wing shape. That is, the airfoil arcuate surface is arranged on the surface side where the air passage expands along the flow of outside air. On the right side, the wind speed distribution of this embodiment is shown for reference.

  Thereby, since the flow of outside air can be bent while reducing the fluid resistance, it is possible to arrange the wind speed control plates 36U and 36B having a larger expansion ratio of the air passage cross-sectional area than in the third embodiment.

  Next, FIG. 10 shows a fifth embodiment of the present invention. In the fifth embodiment, the heat exchanging apparatus of the first embodiment is applied to a room air conditioner for home use, and its configuration is shown in FIG.

  In a room air conditioner for home use, R32 is enclosed as a refrigerant in a refrigeration cycle including a compressor 101, an indoor heat exchanger 106, an expansion valve 103, an outdoor heat exchanger 105, and a four-way valve 108.

  Here, the indoor heat exchanger 106 is housed in the indoor unit 42 installed in the indoor space 34, and other element devices are housed in the outdoor unit 43. Further, in the outdoor unit 43, as in the configuration of the evaporator 104 of the first embodiment, a blower fan 107, an upper wind speed control plate 36U, and a lower wind speed control plate 36B are installed. FIG. 10 shows a cycle in the heating operation. In the cooling operation, the four-way valve 108 rotates 90 degrees clockwise, resulting in a broken line cycle in the figure.

  Next, the operation of this embodiment will be described. In the case of heating operation, the refrigerant discharged from the compressor 101 flows into the indoor heat exchanger 106 via the four-way valve 108, warms the air in the indoor space 34, and is heat-exchanged and cooled. . Thereafter, the refrigerant passes through the expansion valve 103 and becomes low temperature / low pressure, then receives heat from the outside air in the evaporator 104 and evaporates, and flows into the compressor 101 again through the four-way valve 108.

  On the other hand, in the cooling operation, the refrigerant discharged from the compressor 101 flows into the outdoor heat exchanger 105 via the four-way valve 108 and releases heat to the outside air. Depressurized to low pressure. Thereafter, the refrigerant cools the indoor air in the indoor heat exchanger 106 and is heat-exchanged and heated, and finally returns to the compressor 101 via the four-way valve 108.

  In this cycle, the outdoor heat exchanger 105 functions as an evaporator during heating operation and a condenser during cooling operation. In either case, the heat exchanger 105 is provided by a uniform air speed distribution by the air speed control plates 36U and 36B. The refrigerant temperature distribution at the outlet is improved, and as a result, the coefficient of performance (COP) is improved. The above cycle assumes the application of R32, but the same effect can be obtained even when various refrigerants such as R410A are applied.

  As described above, according to the present invention, in the heat exchanger provided with a plurality of refrigerant tubes that are stacked at intervals through the heat exchange fins extending in the vertical direction, the refrigerant flows independently. The wind speed of one or both of the up and down directions of the outside air flowing into the heat exchanger is uniform in at least one or both of the upper and lower regions of the heat exchanger in the space between the outlet side of the exchanger and the blower fan The wind speed control board which controls so that it may be realized was arranged.

  According to this, since it is possible to correct the wind speed distribution of the outside air flowing into the heat exchanger in a direction to make it uniform, the temperature distribution of the refrigerant in the heat exchanger can be made as uniform as possible. Therefore, the proportion of the gas refrigerant in the entire evaporator 104 is reduced, and it is possible to improve the evaporation pressure and improve the coefficient of performance (COP) by improving the heat transfer coefficient of the refrigerant flow path.

  In addition, this invention is not limited to an above-described Example, Various modifications are included. For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Further, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

  2 ... Heat exchange fins, 3 ... Refrigerant pipe, 10 ... Distributor, 11 ... Evaporator inlet channel, 12 ... Refrigerant heat transfer unit, 13 ... Evaporator outlet channel, 14 ... Merger, 30 ... Air channel space, 31 ... Upper air passage, 32 ... Central air passage, 33 ... Lower air passage, 34 ... Indoor space, 35 ... Mounting bracket, 36U ... Upper air speed control plate, 36B ... Lower air speed control plate, 40 ... Heat exchange device, DESCRIPTION OF SYMBOLS 50 ... Heat pump unit, 60 ... Hot water storage unit, 100 ... Heat pump cycle, 101 ... Compressor, 102 ... Water / refrigerant heat exchanger, 103 ... Expansion valve, 104 ... Evaporator, 107 ... Blower fan, 200 ... Water side cycle, 201 ... Hot water storage container, 202 ... Boiling circulation pump, 203 ... Hot water supply port, 204 ... Water pipe.

Claims (10)

A heat exchange device provided in a heat pump for exchanging heat between outside air and refrigerant, wherein the heat exchange device is orthogonal to the heat exchange fins and a plurality of heat exchange fins extending in the vertical direction. A heat exchanger composed of a refrigerant pipe disposed through the heat exchange fin; and a blower fan arranged opposite to the heat exchanger to introduce outside air; In the heat exchange device of the heat pump application device, which is a plurality of refrigerant tubes that are stacked at intervals in the vertical direction of the exchange fins and independently flow the refrigerant,
In the air passage space between the outside air outlet side of the heat exchanger and the blower fan, one of the upper and lower regions of the heat exchanger, or both of the regions in the vertical direction of the outside air flowing into the heat exchanger A heat exchange device for a heat pump application device, characterized in that a wind speed control plate for controlling one or both wind speeds to be uniform is disposed. In the heat exchange device of the heat pump application device according to claim 1,
The wind speed control plate is orthogonal to the arrangement direction (vertical direction) of the heat exchange fins, and has a long side extending along the inner surface on the outside air outlet side of the heat exchanger, and a short side extending along the flow direction of the outside air Formed into a rectangular plate shape having
Further, the wind speed control plate is provided so that the rear end edge of the short side is inclined toward the center side in the vertical direction of the heat exchanger as viewed from the flow of the outside air and along the flow direction of the outside air. A heat exchange device for a heat pump application device. In the heat exchange device of the heat pump application device according to claim 2,
The wind speed control plate is provided in the upper and lower regions of the wind path space, and the upper wind path formed by the upper wind speed control plate and the outer casing of the heat exchange device, and the lower wind speed control plate. And the lower wind passage formed by the outer casing has a cross-sectional area that continuously increases along the flow direction of the outside air, and is sandwiched between the upper wind speed control plate and the lower wind speed control plate. A heat exchange device for heat pump applied equipment, characterized in that the cross-sectional area continuously decreases along the flow direction of outside air. In the heat exchange device of the heat pump application device according to claim 3,
The cross section of the wind speed control plate in the direction orthogonal to the flow of the outside air is any one of a rectangular shape, a shape in which the cross-sectional area increases in an arc shape, and an airfoil shape. Heat exchange device for applied equipment. In the heat exchange device of the heat pump application device according to claim 3,
The arrangement position of the rear edge of the short side of the wind speed control plate is such that the wind speed near the intersection of the average flow velocity distribution line in the vertical direction of the heat exchanger and the wind speed distribution line when the wind speed control plate is not provided. A heat exchange device for a heat pump application device, wherein the heat exchange device is a position of the generated air passage space. In the heat exchange device of the heat pump application device according to claim 3,
Wind speed (U _L ) of the upstream and downstream air passages, inlet side air passage cross-sectional area (A _IN ), outlet side air passage cross-sectional area (A _EX ), average on the inlet side of the entire heat exchanger Is defined using wind speed (U _AVE ) (where wind speed (U _L ) is average wind speed or local wind speed)

A heat exchange device for heat pump application equipment, characterized by satisfying the formula: In the heat exchange device of the heat pump application device according to claim 2,
The length of the long side of the wind speed control plate is not less than the diameter of the blower fan and is determined between 70% and 90% of the lateral length of the outside air outlet surface of the heat exchanger facing the blower fan. A heat exchange device for a heat pump application device. In the heat exchange device of the heat pump application device according to claim 3,
The arrangement position of the wind speed control plate in the vertical direction is arranged within a length range of 1/3 from the upper side and 1/3 from the lower side in the vertical length of the heat exchanger. Heat exchange equipment for heat pump application equipment. In the heat exchange device of the heat pump application device according to claim 2,
The said air speed control board is arrange | positioned only in the area | region below the said heat exchanger, The heat exchange apparatus of the heat pump applied apparatus characterized by the above-mentioned. In the heat exchange device for a heat pump application device according to any one of claims 1 to 9,
The heat exchange device is a heat pump type hot water supply device or a heat exchange device of a heat pump type air conditioner.

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