JP2018096636A - Heat exchanger and refrigeration system using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger which has achieved both a reduced diameter of a flow passage and improvement in heat exchange efficiency by divided flow uniformity, and to provide a refrigeration system using the same.SOLUTION: In a plate fin 2a for constituting a heat exchanger, a first fluid flow passage 11 group is formed by providing a concave groove, and in a header flow passage 8 connected to the first fluid flow passage group, a division flow control pipe 20 and an auxiliary passage pipe 24 in which a refrigerant flows in the header flow passage 8 only during evaporation condition time are provided. Thereby, a reduced diameter of a flow passage cross sectional area of the first fluid flow passage can be achieved and heat exchange efficiency can be improved, and in both cases of the evaporation condition and the condensation condition, a first fluid can surely be divided to the first fluid flow passage group as designed. Thus, a heat exchange rate can be enhanced by adding improvement of heat exchange efficiency by divided flow uniformity.SELECTED DRAWING: Figure 8

Description

  The present invention relates to a heat exchanger and a refrigeration system using the same, and more particularly to a plate fin stacked heat exchanger configured by stacking plate-like plate fins through which a refrigerant flows and a refrigeration system using the same.

  In general, in a refrigeration system such as an air conditioner or a refrigerator, a refrigerant compressed by a compressor is circulated to a heat exchanger such as a condenser or an evaporator to exchange heat with a second fluid for cooling or heating. System performance and energy saving are greatly affected by the heat exchange efficiency of the exchanger. Therefore, high efficiency is strongly demanded for the heat exchanger.

  One of the methods for improving the efficiency of this heat exchanger is to reduce the diameter of the heat transfer tubes through which the heat exchange fluid flows. As another method, for example, the refrigerant that is divided into each heat transfer tube is uniformly distributed. May be diverted to

  Under such circumstances, a heat exchanger of a refrigeration system generally uses a finned tube heat exchanger configured by passing a heat transfer tube through a fin group, and the heat transfer tube has a small diameter. The improvement of heat exchange efficiency and miniaturization are being promoted in order to achieve the same (for example, see Patent Document 1).

  On the other hand, in order to improve the heat exchange efficiency, the heat exchange fluid is divided into a header flow path that guides the heat exchange fluid to each heat transfer tube, and the refrigerant flow to each heat transfer tube is made uniform to make the heat exchange efficiency uniform. (For example, refer patent document 2).

  FIG. 13 shows the heat exchanger described in the above-mentioned Patent Document 2. This heat exchanger 100 is configured by passing a heat transfer tube 102 through a fin group 101, and a flow dividing control tube is connected to the refrigerant inlet side header tube 103. 104 is provided. A plurality of refrigerant distribution openings 105 are arranged in the diversion control pipe 104, and the refrigerant distribution openings 105 are reduced in size as they move away from the refrigerant inlet, so that the refrigerant flowing through the heat transfer pipes 102 is evenly divided. It is like that.

  In this heat exchanger, since the refrigerant is divided at the inlet side of the refrigerant, the refrigerant is diverted to each heat transfer tube while suppressing an increase in the refrigerant temperature due to an increase in pressure loss. The heat exchange efficiency of the heat exchanger used as the evaporator can be improved (if the refrigerant is diverted on the refrigerant outlet side, pressure loss (hereinafter referred to as pressure loss)). As the refrigerant temperature increases, the temperature difference between the second fluid and the second fluid to be exchanged decreases, offsetting the effect of improving the heat exchange efficiency due to the uniform flow, and conversely reducing the heat exchange efficiency. Refrigerant on the side).

JP 2010-78289 A JP 2012-207912 A

  However, the fin-tube heat exchanger described in Patent Document 1 has a limit in reducing the diameter because the heat transfer tube is a tube, and the improvement in heat exchange efficiency due to the decrease in the diameter of the heat transfer tube is approaching the limit. is there.

  However, this heat transfer tube can be easily reduced in diameter if it is a plate fin laminated heat exchanger. That is, the plate fin laminated heat exchanger is formed by pressing a concave groove on the plate fin to form a flow path corresponding to the heat transfer tube, so it is easy to reduce the cross-sectional area of the flow path, The flow path can be made even smaller than the heat transfer tube of the fin tube type heat exchanger.

  Therefore, the applicant studied to improve the heat exchange efficiency by combining the plate fin laminated heat exchanger configured by laminating the plate fins having flow paths with the shunt control pipe described in Patent Document 2.

  However, when the plate fin laminated heat exchanger is used as an evaporator, even if the diversion control pipe is incorporated in the header flow path on the refrigerant inlet side, the diversion effect by the diversion control pipe is not fully exhibited, and heat exchange by diversion is performed. I found that there is a big challenge in improving efficiency.

  The present invention has been intensively studied in view of such points, and has achieved both the reduction of the diameter of the flow path and the improvement of the heat exchange efficiency by the diversion effect, and is highly efficient regardless of whether it is used as an evaporator or a condenser. The purpose is to provide a heat exchanger and a high-performance refrigeration system using the heat exchanger.

In the present invention, in order to achieve the above object, the heat exchanger causes the second fluid to flow between the plate fin stacks of the plate fin stack having the flow path through which the first fluid flows, so that the first fluid and the first fluid A heat exchanger for exchanging heat between two fluids,
The plate fins of the plate fin laminate include a header region in which a header channel A and a header channel B are provided in the header region, and the first fluid between the header channel A and the header channel B in the header region. A plurality of first fluid channels that flow in parallel, and the first fluid channel of the channel region is formed by providing a concave groove in the plate fin,
In addition, when the first fluid evaporates and the first fluid evaporates and condenses, the header flow path A, which is the first fluid inlet, provides a shunt control tube, and the first fluid condenses. Then, an auxiliary passage that communicates with the header flow path A and supplies the first fluid only in the case of the condensing condition is further provided, and the first fluid that flows out of the header flow path A is diverted by the diversion control pipe in the evaporation condition. Under the condensing condition, the refrigerant is supplied to the header channel A from the auxiliary channel as well as the shunt control pipe.

  Thereby, this heat exchanger can improve the heat exchange efficiency by reducing the diameter of the cross-sectional area of the first fluid flow path, and when used as an evaporator, The first fluid can be reliably diverted to the one fluid flow path group as designed, and the heat exchange efficiency can be improved by uniformizing the diversion to increase the heat exchange efficiency.

  That is, this plate fin laminated type heat exchanger has a reduced diameter of the first fluid flow path, and when used as an evaporator, the pressure loss of the first fluid is on the outlet side from the header flow path B on the inflow side. The header flow path A is several times larger. On the other hand, the shunt flow of the first fluid is greatly influenced by the distribution of pressure loss. Therefore, as described above, in this plate fin stacked heat exchanger, even if a flow dividing control pipe is provided in the header flow path B on the inlet side, which is a common sense from the past, the pressure loss of the header flow path A on the outlet side does not occur. Since it is several times higher, the first fluid flowing in the first fluid flow path depends on the pressure loss of the header flow path A on the outlet side, and therefore it cannot be divided as designed. However, in the present invention, since the flow control pipe is provided in the header flow path A on the outlet side where the pressure loss is high based on the understanding of the magnitude of the pressure loss difference and the pressure loss distribution situation in the inlet side / outlet side header flow path, By controlling the pressure loss distribution in the header flow path A that is several times higher, which greatly affects the diversion, the diversion can be made uniform, and the heat exchange efficiency can also be improved by making the diversion uniform.

  In addition, when used as a condenser, the refrigerant flows from the header flow path A on the inlet side in a gas phase state. The refrigerant in the gas phase state is supplied to the header flow path A from the diversion control pipe and at the same time the diversion flow. Since the auxiliary channel is also supplied to the header channel A without going through the control pipe, the refrigerant can be supplied to the first fluid channel group substantially evenly, and the heat exchange efficiency when used as a condenser Can also be improved.

  That is, when used as a condenser, the refrigerant is in a gas phase and the flow velocity is extremely fast, so that the refrigerant flows in a large amount into the header channel A from the end portion side of the shunt control pipe opposite to the refrigerant inlet side. At the same time, since the refrigerant is supplied to the header channel A also from the auxiliary channel, the deviation of the refrigerant in the header channel A portion is eliminated and the header channel A is divided into the first fluid channel group. Therefore, the refrigerant in the header flow path A provided with the diversion control pipe can be prevented from being biased because the refrigerant is in a gas phase state, and the heat exchange efficiency can be reduced even when used as a condenser. Can be improved.

  According to the present invention, the above-described configuration achieves both a reduction in the diameter of the flow path and a uniform flow, and a heat exchanger with high heat exchange efficiency in both evaporation and condensation, and a high-performance, high energy-saving performance using the heat exchanger. A refrigeration system can be provided.

The perspective view which shows the external appearance of the plate fin lamination type heat exchanger in Embodiment 1 of this invention An exploded perspective view showing the plate fin laminated heat exchanger in a separated state Plan view of plate fins constituting plate fin laminate of same plate fin laminate type heat exchanger Exploded view showing part of the configuration of the plate fin The perspective view which cut | disconnects and shows the refrigerant | coolant flow path group part of the plate fin laminated body in the plate fin laminated heat exchanger AA sectional view of FIG. Operation explanatory diagram when using the plate fin laminated heat exchanger as an evaporator Operation explanatory diagram when using the plate fin laminated heat exchanger as a condenser Operation | movement explanatory drawing when using the plate fin lamination type heat exchanger in Embodiment 2 of this invention as an evaporator Operation explanatory diagram when using the plate fin laminated heat exchanger as a condenser Refrigeration cycle diagram of the air conditioner in Embodiment 3 using the plate laminated heat exchanger of the present invention Schematic sectional view of the air conditioner Cross section of conventional heat exchanger

1st invention is a heat exchanger, This heat exchanger flows the 2nd fluid between each plate fin lamination | stacking of the plate fin laminated body which has a flow path through which a 1st fluid flows, The said 1st fluid and the said A heat exchanger for exchanging heat with a second fluid,
The plate fin of the plate fin laminate includes a header region in which a header channel B and a header channel A are provided in the header region, and the first fluid between the header channel B and the header channel A in the header region. A plurality of first fluid channels that flow in parallel, and the first fluid channel of the channel region is formed by providing a concave groove in the plate fin,
In addition, when the first fluid evaporates and the first fluid evaporates and condenses, the header flow path A, which is the first fluid inlet, provides a shunt control tube, and the first fluid condenses. Then, an auxiliary passage that communicates with the header flow path A and supplies the first fluid only in the case of the condensing condition is further provided, and the first fluid that flows out of the header flow path A is diverted by the diversion control pipe in the evaporation condition. Under the condensing condition, the refrigerant is supplied to the header channel A from the auxiliary channel as well as the shunt control pipe.

  Thereby, this heat exchanger can improve the heat exchange efficiency by reducing the diameter of the cross-sectional area of the first fluid flow path, and when used as an evaporator, The first fluid can be reliably diverted to the one fluid flow path group as designed, and the heat exchange efficiency can be improved by uniformizing the diversion to increase the heat exchange efficiency.

  That is, this plate fin laminated type heat exchanger has a reduced diameter of the first fluid flow path, and when used as an evaporator, the pressure loss of the first fluid is on the outlet side from the header flow path B on the inflow side. The header flow path A is several times larger. On the other hand, the shunt flow of the first fluid is greatly influenced by the distribution of pressure loss. Therefore, as described above, in this plate fin stacked heat exchanger, even if a flow dividing control pipe is provided in the header flow path B on the inlet side, which is a common sense from the past, the pressure loss of the header flow path A on the outlet side does not occur. Since it is several times higher, the first fluid flowing in the first fluid flow path depends on the pressure loss of the header flow path A on the outlet side, and therefore it cannot be divided as designed. However, in the present invention, since the flow control pipe is provided in the header flow path A on the outlet side where the pressure loss is high based on the understanding of the magnitude of the pressure loss difference and the pressure loss distribution situation in the inlet side / outlet side header flow path, By controlling the pressure loss distribution in the header flow path A that is several times higher, which greatly affects the diversion, the diversion can be made uniform, and the heat exchange efficiency can also be improved by making the diversion uniform.

  In addition, when used as a condenser, the refrigerant flows from the header flow path A on the inlet side in a gas phase state. The refrigerant in the gas phase state is supplied to the header flow path A from the diversion control pipe and at the same time the diversion flow. Since it is also supplied to the header flow path A from the auxiliary passage not via the control pipe, the refrigerant can be supplied to the first fluid flow path group substantially evenly, and the heat exchange efficiency when used as a condenser is also achieved. Can be improved.

  That is, when used as a condenser, the refrigerant is in a gas phase and the flow velocity is extremely fast, so that the refrigerant flows in a large amount into the header channel A from the end portion side of the shunt control pipe opposite to the refrigerant inlet side. At the same time, since the refrigerant is supplied to the header channel A also from the auxiliary channel, the deviation of the refrigerant in the header channel A portion is eliminated and the header channel A is divided into the first fluid channel group. Therefore, the refrigerant in the header flow path A provided with the diversion control pipe can be prevented from being biased because the refrigerant is in a gas phase state, and the heat exchange efficiency can be reduced even when used as a condenser. Can be improved.

  In a second aspect based on the first aspect, the auxiliary passage is provided with a valve mechanism that closes under an evaporation condition and opens under a condensation condition.

  Thereby, the refrigerant flowing out from the first fluid flow path group to the header flow path A is allowed to flow only from the shunt control pipe during the evaporation condition, and the refrigerant to the header flow path A is also flowed from the auxiliary passage together with the shunt control pipe during the condensation condition. Thus, the flow of the refrigerant can be reliably controlled to be divided.

  According to a third invention, in the second invention, the valve mechanism is a check valve.

  As a result, the refrigerant is automatically stopped in the evaporation condition depending on the flow direction of the refrigerant, and the refrigerant can be allowed to flow in the condensation condition, so that a separate means for controlling the valve mechanism is not required and can be provided at a low cost and the size can be reduced. You can also.

  4th invention is a refrigeration system, This refrigeration system uses the heat exchanger which comprises a refrigerating cycle as the heat exchanger as described in any one of said 1st-3rd invention.

  Thereby, since this refrigeration system has high heat exchange efficiency regardless of whether the heat exchanger is used as a condenser or an evaporator, it can be a high-performance refrigeration system with high energy saving performance.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  Note that the heat exchanger of the present disclosure is not limited to the configuration of the plate fin stacked heat exchanger described in the following embodiments, and is a heat exchanger equivalent to the technical idea described in the following embodiments. The configuration is included.

  The embodiment described below shows an example of the present invention, and the configuration, function, operation, and the like shown in the embodiment are exemplifications and do not limit the present disclosure.

(Embodiment 1)
FIG. 1 is a perspective view showing the appearance of a plate fin laminated heat exchanger (hereinafter simply referred to as a heat exchanger) according to the present embodiment, and FIG. 2 is an exploded perspective view showing the plate fin laminated heat exchanger in a separated state. 3 is a plan view of plate fins constituting the plate fin laminate of the plate fin laminate type heat exchanger, FIG. 4 is an exploded perspective view showing a part of the configuration of the plate fins, and FIG. 5 is a plate fin. The perspective view which cuts and shows the refrigerant | coolant flow path group part of the plate fin laminated body in a laminated heat exchanger, FIG. 6 is AA sectional drawing of FIG. 1, FIG. 7 uses a plate fin laminated heat exchanger as an evaporator. FIG. 8 is an operation explanatory diagram when the plate fin stacked heat exchanger is used as a condenser.

  As shown in FIGS. 1-8, the heat exchanger 1 of this Embodiment is used as a plate fin laminated body 2 comprised by laminating | stacking the several plate fin 2a which is a rectangular plate shape, and an evaporator. In some cases, it has a pipe 5 which becomes an inlet and becomes an outlet when used as a condenser, and a pipe 4 (see FIG. 2) which is the opposite.

  Further, end plates 3a and 3b having substantially the same shape in plan view as the plate fin 2a are provided on both sides (left and right in FIG. 1) of the plate fin laminate 2 in the stacking direction. The end plates 3a and 3b are formed of a rigid plate material, and are formed by metal processing such as aluminum, aluminum alloy, and stainless steel by grinding.

  The end plates 3a and 3b and the plurality of plate fins 2a are integrally joined by brazing in a stacked state.

  In the present embodiment, the end plates 3a and 3b on both sides of the plate fin laminate 2 are connected and fixed at both ends in the longitudinal direction by connecting means 9 such as bolts / nuts or caulking pin shafts. That is, the end plates 3a and 3b on both sides of the plate fin laminate are in a form in which the plate fin laminate 2 is mechanically connected and fixed in a form sandwiching the plate fin laminate 2.

  Further, as will be described later, the plate fin 2a has a plurality of parallel refrigerant flow path groups through which the refrigerant as the first fluid flows, and the first fluid flow path group is substantially U-shaped. The tube 4 and the tube 5 that are formed and connected to the end plate 3a on one side (left side in FIG. 1) of the plate fin laminate 2 are collectively arranged.

  Specifically, as shown in FIG. 3, the plate fin 2a includes a plurality of parallel first fluid flow paths (hereinafter referred to as refrigerant flow paths) 11, header flow paths A8 and header flow paths B10 connected thereto. A pair of formed plate-like members 6a and 6b (see FIG. 4) are brazed and joined to face each other, and the plurality of refrigerant flow paths 11 are formed in a substantially U-shape and are connected to the header flow The path A8 and the header flow path B10 are gathered on one end side.

  And the plate fin 2a of the said structure comprises the plate fin laminated body 2 which laminates | stacks many and makes the main body of a heat exchanger, as shown in FIG. 5, The said plate fin 2a is between each plate fin 2a. A gap through which air as the second fluid flows is formed by a plurality of protrusions 12 (see FIG. 3) provided as appropriate between both ends of the long side 2a and the refrigerant flow path 11.

  In addition, the refrigerant | coolant flow path 11 is formed in the plate-shaped members 6a and 6b by the concave groove | channel, and it can reduce in diameter easily.

  Moreover, between the header flow path A side refrigerant flow path 11a connected to the header flow path A among the refrigerant flow paths 11 and the header flow path B side refrigerant flow path 11b connected to the header flow path B10, heat transfer between them is performed. In order to prevent this, the slit groove 15 is formed.

  Furthermore, in this example, the number of the header flow path A side refrigerant flow paths 11a is increased, and as shown in FIG. 4, the portion facing the passage section 14 of the header flow path A is a non-hole section 16 having no refrigerant flow path. The refrigerant flowing from the flow path 8 to each header flow path 8 side refrigerant flow path 11a collides with the wall 16a of the non-hole portion 16 and flows evenly to each header flow path 8 side refrigerant flow path 11a. is there.

  In the heat exchanger 1 of the present embodiment configured as described above, the refrigerant flows in the refrigerant flow channel 11 group inside each plate fin 2a of the plate fin laminate 2 in parallel in the longitudinal direction and makes a U-turn to return the header. The liquid is discharged from the flow path A8 or the header flow path B10 through the pipe A4 or the pipe B5. On the other hand, the air that is the second fluid passes through the gap formed between the stacks of the plate fins 2 a constituting the plate fin stack 2. Thereby, heat exchange between the refrigerant as the first fluid and the air as the second fluid is performed.

  Here, as shown in FIGS. 6 to 8, in the heat exchanger mainly composed of the plate fin laminate 2 having the above-described configuration, when used as an evaporator, the refrigerant is divided into the header channel A8 on the outlet side. A control tube 20 is provided.

  The diversion control pipe 20 is inserted in the header flow path A8, and its tip is closed. The diversion control pipe 20 is formed of a pipe having a smaller diameter than the inner diameter of the header flow path A8, and forms a refrigerant flow gap 21 between the inner face of the header flow path, and a plurality of diversion ports in the longitudinal direction thereof. 22 are formed at substantially equal intervals.

  The plurality of diversion ports 22 are formed so that the hole diameters become smaller in the direction in which the refrigerant flows, that is, toward the evaporation outlet side when used as an evaporator, that is, in an evaporation condition.

  Further, an auxiliary passage pipe 24 branched from a pipe 23 from the refrigeration system is communicated with the header flow path A8 into which the branch flow control pipe 20 is inserted via a pipe A4 when used as a condenser.

The auxiliary passage pipe 24 is provided with a valve mechanism 25 that is closed when the heat exchanger 1 is used as an evaporator and opened when the heat exchanger 1 is used as a condenser. In this embodiment, the valve mechanism 25 is a check valve that opens and closes by utilizing the fact that the flow direction of the refrigerant is reversed when used as an evaporator and when used as a condenser. 25 is referred to as a check valve 25.

  The check valve 25 does not have to be a check valve as long as it is closed when the heat exchanger 1 is used as an evaporator and opened when used as a condenser. The electric valve may be closed when used as an evaporator and opened when used as a condenser, and is not particularly limited.

  About the heat exchanger comprised as mentioned above, the effect is demonstrated below.

  First, the flow of refrigerant and its action when a heat exchanger is used as an evaporator will be described with reference to FIG.

  The refrigerant flows in from the pipe B5 connected to one end side of the plate fin laminate 2, and flows into the refrigerant flow path 11 group of each plate fin 2a in the liquid phase state via the header flow path B10. The refrigerant that has flowed into the refrigerant flow path 11 group of each plate fin 2a flows out from the pipe A4 to the refrigerant circuit of the refrigeration system in a gas phase state through the header flow path A8.

  When the refrigerant flows through the refrigerant flow path 11, the refrigerant exchanges heat with the air passing between the plate fins 2 a of the plate fin laminate 2.

  Here, in the heat exchanger, the refrigerant gas flowing from the header flow path B10 on the inlet side to the header flow path A8 on the outlet side through the group of refrigerant flow paths 11 is as shown by the arrows in FIG. A pipe that flows from the refrigerant flow gap 21 in the header flow path A8 to the diversion control pipe 20 through a plurality of diversion ports 22 formed in the pipe wall of the diversion control pipe 20, and is connected to the refrigeration system from the outlet side pipe A4. To 23.

  At this time, the refrigerant flowing through the refrigerant circulation gap 21 tries to bypass the auxiliary passage pipe 24 to the pipe 23 connected to the refrigeration system, but the check valve 25 is closed with respect to the refrigerant flow. Without bypassing as described above, the refrigerant from the refrigerant flow path 11 group is subjected to diversion control by the diversion control pipe 20. The diversion port 22 provided in the diversion control pipe 20 is formed so that its hole diameter becomes smaller toward the outlet side, so that the amount of refrigerant flowing through each flow path of the refrigerant flow path 11 group is equalized. To come.

  More specifically, in this heat exchanger, the refrigerant flow path 11 is reduced in diameter, so that the pressure loss of the refrigerant is several times larger in the header flow path A8 on the outlet side than the header flow path B10 on the inlet side. ing. On the other hand, the flow of refrigerant is greatly affected by the distribution of pressure loss. Therefore, this heat exchanger uses the refrigerant flow path 11 because the pressure loss of the header flow path A8 on the outlet side is several times higher even if the branch flow control pipe 20 is provided in the conventional header flow path B10 on the inlet side. Since the flowing refrigerant depends on the pressure loss of the outlet side header flow path A8, it cannot be divided as designed.

  However, in the heat exchanger according to the present embodiment, the branch flow control pipe 20 is provided in the outlet-side header flow path A8 having a high pressure loss, and thus, the outlet-side header flow path having a large influence on the flow is several times higher. The pressure loss distribution in the axial direction in A8 can be controlled to be uniform. Therefore, it is possible to make uniform the flow rate of the refrigerant flowing through each flow path of the refrigerant flow path 11 group.

More specifically, the outlet-side header flow path A8 with high pressure loss is more than the refrigerant flow path 11 of the plate fin farther from the pipe A4 (the refrigerant flow path of the plate fin closer to the right in FIG. 7). The refrigerant flows more easily in the refrigerant flow path 11 of the plate fin closer to the tube A4 (the refrigerant flow path of the plate fin closer to the left in FIG. 7). In other words, the flow rate of the refrigerant may be uneven.

  However, the flow dividing control pipe 20 is inserted into the header flow path A8 on the outlet side, and the opening area of the flow outlet 22a on the most outlet side of the flow dividing control pipe 20 is as shown in FIG. Since the pressure loss of the refrigerant passing through the diversion port is increased by making the diameter smaller than the counter-exit side (portion closer to the right side in FIG. 7), the refrigerant flow does not drift as described above. The amount of refrigerant in the first fluid channel 11 can be equalized.

  As a result, this heat exchanger can improve the heat exchange efficiency in the refrigerant flow path 11 group portion, and can be a heat exchanger with higher heat efficiency.

  Next, the flow of refrigerant and its action when the heat exchanger is used as a condenser will be described with reference to FIG.

  The refrigerant passes through the branch flow control pipe 20 provided in the header flow path A8 on the inflow side from the pipe 23 of the refrigeration system through the pipe A4 connected to the one end portion side of the plate fin laminate 2, and its flow outlet. 22, and flows from the refrigerant circulation gap 21 to the refrigerant flow path 11 group of each plate fin 2 a. The refrigerant that has flowed into the refrigerant flow path 11 group of each plate fin 2a flows out from the pipe B5 to the refrigerant circuit of the refrigeration system via the header flow path B10 on the outlet side.

  When the refrigerant flows through the refrigerant flow path 11, the refrigerant exchanges heat with the air passing between the plate fins 2 a of the plate fin laminate 2.

  Here, since the refrigerant flowing through the branch flow control pipe 20 is in a gas phase state, the flow velocity is extremely fast compared to that in the liquid phase state, and the branch port 22 on the side opposite to the inlet side (portion closer to the right side in FIG. 8). The number of the diversion outlets increases. Moreover, the diversion port 22 is larger on the side opposite to the inlet side. Therefore, the refrigerant flows more toward the side opposite to the inlet side of the refrigerant flow path 11 group, and does not flow evenly. That is, when the diversion control pipe 20 used for evenly dispersing when used as an evaporator is used as a condenser, the diversion variation is promoted to the refrigerant flow path 11 group.

  However, in this heat exchanger, the auxiliary passage pipe 24 branched from the pipe 23 of the refrigeration system communicates with the refrigerant flow gap 21 of the header flow path A8 through which the refrigerant flows into the refrigerant flow path 11 group. Since the check valve 25 provided in the pipe 24 is open with respect to the refrigerant flow, the refrigerant from the pipe 23 of the refrigeration system is bypassed to the outlet side portion of the refrigerant flow gap 21.

  As a result, the refrigerant can sufficiently flow also to the outlet side portion (the portion close to the left side in FIG. 8) of the refrigerant flow path 11 group. That is, the variation in the diversion by the diversion control pipe 20 is offset.

  As a result, the heat exchanger improves the heat exchange efficiency in the refrigerant channel 11 group even when used as a condenser, and heat exchange with high heat efficiency is the same as when used as an evaporator. Can be a container.

  Further, in this embodiment, the configuration for equalizing the refrigerant flow distribution by the flow dividing control pipe 20 described above is merely a perforation of the flow dividing port 22 in the flow dividing control pipe 20, so that the structure is simple and can be provided at low cost. .

In the heat exchanger of the present embodiment, it is assumed that the refrigerant flow path 11 group makes a U-turn, but this does not make a U-turn, and the header flow path A and the header flow path B are assumed to be linear. It may be provided separately on the left and right ends of the plate fins. The heat exchanger configured as described above also has the effect of making the refrigerant flow path 11 group U-shaped, that is, the heat flow efficiency is improved by lengthening the refrigerant flow path while shortening the overall length of the plate fin and making it compact. Except for the enhancement effect, the detailed configuration and effects are the same as those described in the above embodiment, and the same reference numerals are given to portions having the same functions as in the above embodiment, and the description is omitted.

(Embodiment 2)
FIG. 9 is a diagram for explaining the operation when the plate fin laminated heat exchanger according to Embodiment 2 of the present invention is used as an evaporator, and FIG. 10 shows the use of the plate fin laminated heat exchanger as a condenser. It is operation | movement explanatory drawing when there is.

  In the second embodiment, when used as an evaporator, it becomes the inlet side, and when used as a condenser, the header flow path B10 on the outlet side is also provided with a condensing diversion control pipe 30 as shown by the broken lines in FIGS. It is provided.

  When the heat exchanger is used as a condenser, the condensing diversion control pipe 30 functions as a diversion action by the condenser diversion port 31, and the diversion equalization action by the auxiliary passage pipe 24 described in the first embodiment. In addition, the diversion action by the diversion port 31 for the condenser is added, so that the refrigerant flowing through the refrigerant flow path 11 group can be made more efficient and uniform. Therefore, the heat exchange efficiency in the refrigerant flow path 11 group part when using as a condenser improves further, and it can be set as a heat exchanger with high heat efficiency.

  As described above, when the condensing diversion control pipe 30 is used as an evaporator, even if it is provided, the pressure loss of the header channel B5 is small and the diversion effect is hardly exhibited. In the heat exchanger, as described in the first embodiment, the heat exchange efficiency is improved by the diversion action by the diversion control pipe 20 provided in the header flow path A8.

(Embodiment 3)
The third embodiment is a refrigeration system configured using any one of the heat exchangers of the first and second embodiments described above.

  In this embodiment, an air conditioner will be described as an example of a refrigeration system. FIG. 11 is a refrigeration cycle diagram of the air conditioner, and FIG. 12 is a schematic cross-sectional view showing the indoor unit of the air conditioner.

  In FIG. 11 and FIG. 12, the air conditioner includes an outdoor unit 51 and an indoor unit 52 connected to the outdoor unit 51. The outdoor unit 51 includes a compressor 53 that compresses the refrigerant, a four-way valve 54 that switches a refrigerant circuit during cooling and heating operation, an outdoor heat exchanger 55 that exchanges heat between the refrigerant and the outside air, a decompressor 56 that decompresses the refrigerant, A blower 59 is provided. The indoor unit 52 is provided with an indoor heat exchanger 57 that exchanges heat between the refrigerant and the indoor air, and an indoor blower 58. The compressor 53, the four-way valve 54, the indoor heat exchanger 57, the decompressor 56, and the outdoor heat exchanger 55 are connected by a refrigerant circuit to form a heat pump refrigeration cycle.

  In the refrigerant circuit according to the present embodiment, tetrafluoropropene or trifluoropropene is used as a base component, and difluoromethane, pentafluoroethane, or tetrafluoroethane is preferably used so that the global warming potential is 5 or more and 750 or less. A refrigerant in which two components or three components are mixed is used so that it is 350 or less, more desirably 150 or less.

During the cooling operation, the air conditioner switches the four-way valve 54 so that the discharge side of the compressor 53 and the outdoor heat exchanger 55 communicate with each other. As a result, the refrigerant compressed by the compressor 53 becomes a high-temperature and high-pressure refrigerant and is sent to the outdoor heat exchanger 55 through the four-way valve 54. Then, heat is exchanged with the outside air to dissipate the heat, and a high-pressure liquid refrigerant is sent to the decompressor 56. In the decompressor 56, the pressure is reduced to form a low-temperature and low-pressure two-phase refrigerant, which is sent to the indoor unit 52. In the indoor unit 52, the refrigerant enters the indoor heat exchanger 57, exchanges heat with the indoor air, absorbs heat, evaporates, and becomes a low-temperature gas refrigerant. At this time, the room air is cooled to cool the room. Further, the refrigerant returns to the outdoor unit 51 and is returned to the compressor 53 via the four-way valve 54.

  During the heating operation, the four-way valve 54 is switched so that the discharge side of the compressor 53 and the indoor unit 52 communicate with each other. Thereby, the refrigerant compressed by the compressor 53 becomes a high-temperature and high-pressure refrigerant, passes through the four-way valve 54, and is sent to the indoor unit 52. The high-temperature and high-pressure refrigerant enters the indoor heat exchanger 57, exchanges heat with room air, dissipates heat, and is cooled to become high-pressure liquid refrigerant. At this time, the room air is heated to heat the room. Thereafter, the refrigerant is sent to the decompressor 56, and is decompressed by the decompressor 56 to become a low-temperature and low-pressure two-phase refrigerant, sent to the outdoor heat exchanger 55, exchanges heat with the outside air, evaporates, and passes through the four-way valve 54. Then, it is returned to the compressor 53.

  The air conditioner configured as described above uses either the outdoor heat exchanger 55 or the indoor heat exchanger 57 for one or both of the heat exchangers described in the above embodiments, so that either the evaporation or the condensation can be performed. In this case, high heat exchange efficiency is exhibited, and a high-performance refrigeration system with high energy saving performance can be obtained.

  As mentioned above, although the heat exchanger concerning this invention and the refrigerating system using the same were demonstrated using the said embodiment, this invention is not limited to this. That is, the embodiment disclosed this time should be considered as illustrative and not restrictive in all respects, and the scope of the present invention is indicated by the scope of the claims rather than the above description. It is intended that all modifications within the meaning and scope equivalent to the terms of the claims are included.

  The present invention provides both a heat exchanger with high heat exchange efficiency in both evaporation and condensation, and a high-performance refrigeration system with high energy-saving using the same, in which both the diameter of the flow path is reduced and the flow is made uniform. can do. Therefore, it can be widely used in heat exchangers and various refrigeration equipment used for home and commercial air conditioners, and has a great industrial value.

DESCRIPTION OF SYMBOLS 1 Heat exchanger 2 Plate fin laminated body 2a Plate fin 3, 3a, 3b End plate 4 Tube A
5 Tube B
6a First plate member 6b Second plate member 8 Header flow path A
9 Connecting means 10 Header flow path B
11 Refrigerant channel (first fluid channel)
11a Header flow path A side refrigerant flow path 11b Header flow path B side refrigerant flow path

12 Protrusion 14 Passage 15 Slit groove 16 Non-hole 16a Wall 20 Split flow control pipe 21 Refrigerant flow gap 22, 22a Split outlet 23 Pipe 24 Auxiliary path
25 Valve mechanism (check valve)
30 Condensation branch control pipe 31 Condenser branch

Claims (4)

A heat exchanger for causing a second fluid to flow between each plate fin stack of a plate fin stack having a flow path through which the first fluid flows, and exchanging heat between the first fluid and the second fluid,
The plate fins of the plate fin laminate include a header region in which a header channel A and a header channel B are provided in the header region, and the first fluid between the header channel A and the header channel B in the header region. A plurality of first fluid channels that flow in parallel, and the first fluid channel of the channel region is formed by providing a concave groove in the plate fin,
In addition, when the first fluid evaporates and the first fluid evaporates and condenses, the header flow path A, which is the first fluid inlet, provides a shunt control tube, and the first fluid condenses. Then, an auxiliary passage that communicates with the header flow path A and supplies the first fluid only in the case of the condensing condition is further provided, and the first fluid that flows out of the header flow path A is diverted by the diversion control pipe in the evaporation condition. The heat exchanger is configured to supply the refrigerant to the header channel A from the auxiliary channel together with the branch flow control tube under the condensation condition.   The heat exchanger according to claim 1, wherein the auxiliary passage is provided with a valve mechanism that closes under an evaporation condition and opens under an condensation condition.   The heat exchanger according to claim 2, wherein the valve mechanism is a check valve.   The refrigeration system which used the heat exchanger which comprises a refrigerating cycle as the heat exchanger in any one of the said 1st-3rd.

Images