JP6827186B2 - Plate fin laminated heat exchanger and refrigeration system using it - Google Patents

Description

The present invention relates to a plate fin laminated heat exchanger and a refrigeration system using the same.

Generally, in a refrigerating 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. The heat exchange efficiency of the exchanger greatly affects the performance and energy saving of the system. Therefore, heat exchangers are strongly required to have high efficiency.

Under such circumstances, as a heat exchanger of a refrigeration system such as an air conditioner or a refrigerator, a fin tube type heat exchanger configured by penetrating a heat transfer tube through a fin group is generally used. Therefore, the heat exchange efficiency is being improved and the size is being reduced by reducing the diameter of the heat transfer tube.

However, since there is a limit to the reduction in diameter of the heat transfer tube, improvement of heat exchange efficiency and miniaturization are approaching the limit.

On the other hand, among the heat exchangers used for exchanging heat energy, a plate fin laminated heat exchanger configured by laminating plate fins having a flow path is known.

This plate fin laminated heat exchanger exchanges heat between the refrigerant flowing through the flow path formed in the plate fins and the second fluid flowing between the laminated plate fins, and the amount of cold is small. It is used in an air conditioner for vehicles having a low refrigerant pressure (see, for example, Patent Document 1).

10A and 11B show a plate fin laminated heat exchanger described in Patent Document 1, and the heat exchanger 100 has a large number of plate fins 102 having a heat transfer flow path 101 (see FIG. 11) through which a refrigerant flows. The end plates 104 are laminated on both end faces of the laminated plate fin laminate 103, and the inflow side header flow path 105 and the outflow side header flow path 106 are formed at both left and right ends of the heat transfer flow path 101. ..

Utility Model Registration No. 3192719

In the plate fin laminated heat exchanger described in Patent Document 1, since the flow path 101 is formed by press-molding a concave groove in the plate fin 102, the cross-sectional area of the heat transfer flow path 101 is transferred to the fin tube type. It can be made smaller than a heat tube, and the heat exchange efficiency can be improved and the size can be reduced.

However, in the plate fin 102 of the plate fin laminated heat exchanger described in Patent Document 1, the inflow and outflow header flow paths 105 and 106 of the refrigerant flowing through the heat transfer flow path 101 are divided into the left and right ends of the plate fin 102. Since the flow path length is short and the heat exchange efficiency between the refrigerant and air is low, the length dimension of the plate fin 102 becomes large if the flow path length is to be lengthened. It was something that would end up.

Therefore, as shown in FIG. 12, the applicant provides header flow paths 105 and 106 for inflow and outflow of the refrigerant together on one end side of the plate fin 102, and makes a U-turn on the heat transfer flow path 101 on the other end side to flow out. As a configuration for connecting to the header flow paths 105 and 106, the dimensions of the plate fins 102 are shortened while increasing the length of the heat transfer flow path 101 to improve the heat exchange efficiency between the refrigerant and air and at the same time promote further miniaturization. I am considering to be able to do it.

In this case, the heat transfer flow path 101 makes a U-turn on the other end side of the plate fin 102, and the heat transfer flow path 101a connected to the inflow header flow path 105 and the heat transfer return flow path 101b connected to the outflow header flow path 106 Since the heat transfer channels 101a and 101b are adjacent to each other, a slit-shaped heat insulating groove 107 is required to prevent heat from moving between the heat transfer channels 101a and 101b. When the slit-shaped heat insulating groove 107 is provided, the portion of the plate fin 102 on the heat transfer forward flow path 101a side and the heat transfer return flow path 101b side are separated by the slit of the heat transfer groove 107, and both portions are separated. Since the shape is as shown in the above, the work of laminating the plate fins 102 is hindered.

Therefore, the heat insulating groove 107 has connecting portions 108 left at several points in the longitudinal direction thereof, and the laminated plate fins 102 and the end frates 104 provided on both side end faces thereof are brazed and integrated in a welding furnace to integrate the plate fin laminated body. After constructing the above, a press blade is inserted from above the one end plate 104 to press-cut the connecting portion 108 of the heat insulating groove 107. Therefore, as shown in FIG. 13, the end plate 104 is formed with a slit groove 109 having the same shape as the heat insulating groove 107 of the plate fin 102.

However, since the end plate 104 is thicker than the plate fin 102, a slit groove is formed in the slit groove 109 having the same groove width as the heat insulating groove 107 of the plate fin 102 during press working to create the end plate 104. The press blade is broken, and the slit groove 109 cannot be machined at the same time, which requires post-processing, resulting in high cost.

In order to solve this problem, the groove width of the heat insulating groove 107 provided in the plate 102a of the plate fin 102 may be widened, but the plate 102a is joined to the end plate 104 to form a flow path recess as shown in FIG. Since the groove 110 is closed to form the heat transfer flow path 101, if the groove width of the heat insulating groove 107 of the plate 102a of the plate fin 102 is widened together with the slit groove of the end plate 104, the end plate 104 is shown in FIG. The joint allowance (joint area) between the plate fin 102 and the plate 102a is reduced by the width of the broken line shown in Z, and the joint between the end plate 104 and the plate 102a of the plate fin 102 is easily peeled off by the refrigerant pressure, resulting in pressure resistance. It will drop. Therefore, the groove width of the slit groove 109 of the end plate 104 cannot be widened, and only the slit groove 109 of the end plate 104 is widened, and the end plate 104 must be punched by a press and then post-processed by cutting or the like. However, there is a problem that the processing man-hours increase and the cost increases.

Further, if the slit groove width of the end plate 104 is widened and the slit groove width of the plate fin 102 is also widened according to the slit groove width of the end plate 104, the width direction dimension of the plate fin 102 is increased by the widening of the groove width. This will reduce the miniaturization effect obtained by using the plate fin laminated heat exchanger. That is, there is a problem that it is difficult to achieve both the workability of the end plate 104 and the pressure resistance of the plate fin 102 without deteriorating the miniaturization effect of the heat exchanger.

The present invention has been made in view of these points, and an object of the present invention is to solve the problems of ensuring the workability of the end plate and the pressure resistance of the plate fins, and to solve the problems of being inexpensive, highly reliable, and compact. It is an object of the present invention to provide a highly efficient plate fin laminated heat exchanger and a freezing system using the same.

In order to achieve the above object, the present invention constitutes a plate fin laminate by laminating a large number of plate fins having a plurality of heat transfer channels connected to a pair of inflow and outflow header channels, and the plate fin laminates. It is a plate fin laminated heat exchanger in which end plates are joined and integrated on both side end faces of the body, and the plate fins are connected to a pair of header flow paths by joining plates having a plurality of flow path forming concave grooves. Along with forming a heat transfer flow path, the heat transfer flow path forms a U-turn-shaped heat transfer flow path on each plate, and a pair of header flow paths connected to the heat transfer flow path are collectively provided on one end side of the plate fins. A slit-shaped heat insulating groove is formed between the forward flow path and the return flow path of the U-turn-shaped heat transfer flow path of the plate fin, and the plate fins on both end faces of the plate fin laminate form a flow path. A thin plate provided with a heat insulating slit groove facing the heat insulating groove of the plate fin is joined to a plate having a concave groove to form a heat transfer flow path, and the plate fins on both side end faces are formed through the thin plate. It is joined to the end plate, and the end plate is provided with a slit groove at a position facing the heat insulating groove of the plate fin and the heat insulating slit groove of the thin plate, and the slit groove is for heat insulating the heat insulating groove of the plate fin and the heat insulating of the thin plate. The groove width is wider than the slit groove.

As a result, the groove for forming the flow path provided in the plate fin to be joined to the end plate can be closed by the thin plate to form the heat transfer flow path, so that the groove width of the slit groove for heat insulation provided in the thin plate can be changed to the plate. The width dimension is the same as the groove width of the slit groove provided in the fin, and the joint allowance (joint area) with the plate fin is maintained to ensure pressure resistance, and at the same time, the slit groove width of the plate fin is kept to the minimum necessary groove width. , It is possible to suppress the increase in the width dimension of the plate fin and maintain the miniaturization effect. Since it is not necessary for the end plate to close the concave groove for forming the flow path of the plate fin, the groove width of the slit groove is widened to eliminate the breakage of the press blade for forming the slit groove and press the end plate. Slit grooves can be formed at the same time during machining, and workability can be improved and the slit groove can be provided at low cost.

According to the above configuration, the present invention achieves both workability of the end plate and ensuring pressure resistance of the plate fins without deteriorating the miniaturization effect of the heat exchanger, and is inexpensive, highly reliable, compact and highly efficient. It can be a plate fin laminated heat exchanger and a refrigeration system using it.

A perspective view showing the appearance of the plate fin laminated heat exchanger according to the first embodiment of the present invention. An exploded perspective view of the plate fin laminated heat exchanger (A) (b) Perspective view of each plate constituting the plate fin of the plate fin laminated heat exchanger. A perspective view showing a laminated state of plate fins in the plate fin laminated heat exchanger. An exploded perspective view showing a laminated state of plate fins in the plate fin laminated heat exchanger. An exploded perspective view showing plates, thin plates, and end plates located on both end faces of the plate fin laminated heat exchanger. Enlarged cross-sectional view of the main part showing the joint state of the plates, thin plates, and end plates located on both end faces of the plate fin laminated heat exchanger. Refrigerating cycle diagram of the air conditioner according to the second embodiment using the plate laminated heat exchanger of the present invention. Schematic cross-sectional view of the air conditioner Cross-sectional view of a conventional plate fin laminated heat exchanger Top view of plate fins in the conventional plate fin laminated heat exchanger Plan view of plate fins proposed by the applicant An exploded perspective view showing the plate and end plate of the plate fins. Enlarged perspective view showing the joint between the plate of the plate fin and the end plate. Enlarged cross-sectional view of the main part showing the joint state of the plate fin and the end plate

The first invention is a heat exchanger, in which a large number of plate fins having a plurality of heat transfer channels connected to a pair of inflow and outflow header channels are laminated to form a plate fin laminate. It is a plate fin laminated heat exchanger in which end plates are joined and integrated on both side end faces of the plate fin laminated body, and the plate fins are joined by joining plates having a plurality of flow path forming concave grooves. A heat transfer flow path connecting to the pair of header flow paths is formed, and the heat transfer flow path forms a U-turn-shaped heat transfer flow path on each plate, and the pair of header flow paths connected to the heat transfer flow path are connected to one end side of the plate fin. In addition, a slit-shaped heat insulating groove is formed between the forward flow path and the return flow path of the U-turn-shaped heat transfer flow path of the plate fin, and both end faces of the plate fin laminate are formed. The plate fins of the above are formed by joining a thin plate provided with a heat insulating slit groove facing the heat insulating groove of the plate fin to a plate having a concave groove for forming a flow path to form a heat transfer flow path, and plate fins on both end faces thereof. Is joined to the end plate via the thin plate, the end plate is provided with a slit groove at a position facing the heat insulating groove of the plate fin and the heat insulating slit groove of the thin plate, and the slit groove is the heat insulating groove of the plate fin. The groove width is wider than the groove and the heat insulating slit groove of the thin flat plate.

As a result, the groove for forming the flow path provided in the plate fin to be joined to the end plate can be closed by the thin plate to form the heat transfer flow path, so that the groove width of the slit groove for heat insulation provided in the thin plate can be changed to the plate. The width dimension is the same as the groove width of the slit groove provided in the fin, and the joint allowance (joint area) with the plate fin is maintained to ensure pressure resistance, and at the same time, the slit groove width of the plate fin is kept to the minimum necessary groove width. , It is possible to suppress the increase in the width dimension of the plate fin and maintain the miniaturization effect. Since it is not necessary for the end plate to close the concave groove for forming the flow path of the plate fin, the groove width of the slit groove is widened to eliminate the breakage of the press blade for forming the slit groove and press the end plate. Slit grooves can be formed at the same time during machining, and workability can be improved and the slit groove can be provided at low cost.

In the second invention, in the first invention, the thin flat plate is formed by using a plate fin base plate of plate fins.

As a result, both the plate fin and the thin plate that close the groove for forming the flow path are in a state where an adhesive such as a brazing material is applied, so that the plate fin and the thin plate can be reliably joined. It becomes strong, and the peeling prevention effect between the plate fin and the thin flat plate can be enhanced to further improve the pressure resistance.

In the third invention, in the first invention, the thin flat plate is formed by using a plate material thinner than the end plate and thicker than the plate fins.

As a result, the thin flat plate is thicker than the plate fins and has stronger rigidity than the plate fins, so that it also functions as an end plate, and the plate thickness of the end plate itself is reduced by that amount to press the slit groove of the end plate. The sex can be improved.

A fourth invention is a refrigeration system, in which the heat exchanger constituting the refrigeration cycle is a plate fin laminated heat exchanger according to any one of the first to third inventions.

As a result, in this refrigeration system, the heat exchanger of the plate fin laminated heat exchanger is inexpensive, has high pressure resistance, and is compact and highly efficient, so that it is inexpensive, highly reliable, and highly energy efficient. It can be a system.

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

The heat exchanger of the present disclosure is not limited to the configuration of the plate fin laminated heat exchanger described in the following embodiments, and has the same heat as the technical idea described in the following embodiments. It includes the configuration of the exchanger.

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

(Embodiment 1)
FIG. 1 is a perspective view showing the appearance of the plate fin laminated heat exchanger according to the first embodiment of the present invention, FIG. 2 is an exploded perspective view of the plate fin laminated heat exchanger, and FIGS. 3 (a) and 3 (b) are plates. A perspective view of each plate constituting the plate fins of the fin laminated heat exchanger, FIG. 4 is a perspective view showing a laminated state of plate fins in the plate fin laminated heat exchanger, and FIG. 5 is a perspective view of the plate fin laminated heat exchanger. An exploded perspective view showing a laminated state of plate fins, FIG. 6 is an exploded perspective view showing plates, thin plates, and end plates located on both end faces of a plate fin laminated heat exchanger, and FIG. 7 is a plate fin laminated heat exchanger. It is an enlarged cross-sectional view of the main part which shows the joint state of the plate, the thin plate, and the end plate located on both side end faces of.

As shown in FIGS. 1 and 2, in the heat exchanger 1 of the present embodiment, end plates 3a and 3b having substantially the same plan view are joined and integrated on both sides of a substantially bow-shaped plate fin laminate 2. It is composed of. A tube A4, which serves as an inlet when used as an evaporator and an outlet when used as a condenser, and a tube B5 which vice versa are provided on one end side of a substantially bow-shaped rectangle.

The end plates 3a and 3b on both sides of the plate fin laminate 2 are brazed so as to sandwich the plate fin laminate 2, and both ends in the longitudinal direction are connected and fixed by fastening means 9 such as bolts, nuts or caulking pin shafts. However, it retains the rigidity as a heat exchanger.

Further, the plate fins 2a constituting the plate fin laminate 2 are a heat transfer flow in which a first fluid (hereinafter, referred to as a refrigerant) such as a refrigerant flows by joining a pair of plates 6a and 6b shown in FIG. 3 by brazing or the like. It has a structure having a path, and as shown in FIGS. 4 and 5, a large number of layers are laminated to form a stacking interval in which a second fluid such as air (hereinafter referred to as air) flows between the plate fins 2a. .. Then, heat is exchanged between the refrigerant flowing through the heat transfer flow path provided in the plate fins 2a and the air flowing through the stacking gap between the plate fins 2a.

As shown in FIG. 5, the pair of plates 6a and 6b constituting the plate fins 2a are provided on one of the plates 6a at the openings 8a and 10a serving as the header flow path A8 and the header flow path B10 and the opening edges thereof. The ring-shaped concave grooves 8b and 10b, the connecting flow path concave groove 11a derived from the ring-shaped concave grooves 8b and 10b, and the branch flow path concave groove 12a provided at the end of the connecting flow path concave groove 11a. A plurality of substantially U-shaped parallel groove forming concave grooves 14a branched from the dividing channel concave groove 12a are provided.

On the other hand, the other plate 6b has openings 8c and 10c serving as header flow paths A8 and header flow paths B10, ring-shaped concave grooves 8d and 10d provided at the openings edges thereof, and concave grooves for connecting flow paths of the plate 6a. A groove 12b for branch flow path located at a portion facing the end portion of 11a and a plurality of concave grooves 14b for forming flow paths that are branched and formed from the concave groove 12b for branch flow path and are parallel to each other in a substantially U shape are provided. ..

The pair of plates 6a and 6b are formed by the ring-shaped concave grooves 8b, 10b and 8d, 10d provided at the openings 8a, 10a and 8c, 10c and the opening edges thereof, and the groove 12a and 12b for the branch flow path. The groove 14a and 14b for forming a flow path are joined by brazing so as to match each other, and at the openings 8a, 10a, 8c, 10c and the ring-shaped concave grooves 8b, 10b, 8d, 10d at the opening edge. The header flow path A8 and the header flow path B10 are formed, and the branch flow path 12a and 12b and the flow path forming concave grooves 14a and 14b form the branch flow path 12 and the heat transfer flow path 14, and the communication flow path concave. The grooves 11a and 11b form a connecting flow path 11.

The plate fins 2a of the plate fin laminated body 2 having the above configuration form a stacking interval in which air flows by a plurality of protrusions 15 (see FIG. 3) appropriately provided along the longitudinal direction of the plate fins 2a.

Here, as shown in the overall view of the plate fins of FIG. 3, the heat transfer flow path 14 has a shape that is bent in a substantially bow shape and then makes a U-turn, similar to the outer shape of the plate fins 2a, and as shown in FIG. A slit-shaped heat insulating groove 16 that prevents heat transfer between the heat transfer forward flow path 14-1 group connected to the header flow path A8 and the heat transfer return flow path 14-2 group connected to the header flow path B10. Is formed.

Further, the heat insulating groove 16 is formed in a state where the plate fins 2a are in the state of parts, that is, when one plate fin 2a is used, connecting portions 17 are left at several places in the longitudinal direction thereof, and heat transfer flow flows on both sides of the heat insulating groove 16. The passage 14-1 portion and the heat transfer return flow path 14-2 portion are connected. Then, the end plates 3a and 3b provided on both side end faces of the plate fin laminated body 2 formed by laminating the plate fins 2a also face the heat insulating groove 16 in order to insert a press blade for cutting the connecting portion 17 of the heat insulating groove 16. A slit groove 18 having the same shape as this is provided at the position where the slit groove 18 is formed.

Further, the end plates 3a and 3b on both end surfaces of the plate fin laminate 2 are brazed to the plate fins 2a with a thin plate 19 having the same shape as the plate fins 2a and made of the same aluminum as the plate fins 2a. It is joined and integrated.

As shown in FIG. 6, the thin flat plate 19 has a heat insulating slit groove 20 having the same shape formed at a position facing the heat insulating groove 16 of the plate fin 2a, and the groove width thereof is as shown in FIG. The dimensions are the same as the groove width l of the heat insulating groove 16 of the plate fin 2a.

On the other hand, the groove width of the slit groove 18 provided in the end plate 3a is a groove width L sufficiently wider than the groove width of the heat insulating groove 16 of the plate fin 2a and the heat insulating slit groove 20 of the thin plate 19.

In this example, the thin flat plate 19 is made of a plate fin material having no recessed grooves or the like constituting a heat transfer flow path or the like, and has a thin plate thickness similar to that of the plate fin 2a, but is limited to this. It is composed of a plate material made of the same material as the end plates 3a and 3b, and the plate thickness is such that the press blade does not break even if the heat insulating slit groove 20 has the same groove width as the heat insulating groove 16 of the plate fin 2a. It may have the thickness of.

Next, the action and effect of the plate fin laminated heat exchanger configured as described above will be described by taking as an example the case where the plate fin laminated heat exchanger is used as the heat exchanger of the refrigeration system.

When the heat exchanger of the present embodiment is used, for example, under evaporation conditions, a gas-liquid two-phase refrigerant flows from the pipe A4 into the header flow path A8 on the inlet side of the plate fin laminate 2. As is clear from the flow path configurations shown in FIGS. 7 and 8, the refrigerant that has flowed into the header flow path A8 flows into the heat transfer flow path 14 group via the communication flow path 11 and the branch flow path 12 of each plate fin 2a. .. The refrigerant flowing into the heat transfer flow path 14 group of each plate fin 2a makes a U-turn and flows out from the pipe B5 to the refrigerant circuit of the refrigeration system in a gas phase state through the header flow path B10.

Then, when flowing through the heat transfer flow path 14, the refrigerant exchanges heat with the air passing through the plate fin stacking interval of the plate fin laminate 2.

Although heat exchange is performed as described above, the heat transfer flow path 14 formed on the outermost end surface of the plate fin laminate 2 among the heat transfer flow paths 14 for the refrigerant flow path that exchanges heat with air is shown in FIG. 7. As shown in the above, the groove 14a for forming a flow path of the plate fin 2a is covered with a thin flat plate 19 interposed between the end plate 3a and the plate fin 2a. The thin flat plate 19 is made of the same material as the plate fins 2a and is thin.

Therefore, it is possible to sufficiently secure the joining allowance (joining area) between the thin plate 19 and the plate fins 2a by making the groove widths of the heat insulating slit groove 20 of the thin plate 19 and the heat insulating groove 16 of the plate fins 2a the same.

Therefore, the pressure resistance of the joint portion between the thin flat plate 19 and the plate fin 2a without peeling can be made sufficient. That is, since the thin flat plate 19 that closes the flow path forming concave groove 14a of the plate fin 2a is a thin plate of the same aluminum as the plate fin 2a, the heat insulating slit groove 20 has the same width as the heat insulating groove 16 of the plate fin 2a. Even if the groove width is narrow, there is no problem such as the press blade breaking, and the groove width of the heat insulating slit groove 20 is reduced to secure the joining allowance (joining area) with the plate fin 2a and to have sufficient pressure resistance. Can be.

On the other hand, since the end plate 3a forms the heat transfer flow path 14 by closing the flow path forming concave groove 14a of the plate fin 2a with the thin plate 19, the slit groove 18 has a joint allowance (joint area) with the plates 6a and 6b. ) Can be widened without worrying about the decrease. Therefore, the press blade forming the slit groove 18 of the end plate 3a can be widened so as not to break, and the slit groove 18 can be formed at the same time as the press working of the end plate 3a, reducing the processing man-hours, that is, The workability of the end plate 3a can be improved.

Further, in the present embodiment, since the thin flat plate 19 is formed by using the plate fin base plate, the thin flat plate 19 is also coated with a bonding material such as a brazing material like the plate fin 2a. The joint between 19 and the plate fin 2a can be made reliable and strong, and the pressure resistance can be made higher.

Further, if the thin plate 19 is thinner than the end plate 3a and thicker than the plate fins 2a, the thin plate 19 thicker than the plate fins 2a has a stronger rigidity than the plate fins 2a. Like the plate 3a, it also serves as a strength member. Therefore, the thickness of the end plate 3a can be reduced by that amount to improve the workability of the end plate 3a by pressing. In this case, the thickness of the thin flat plate 19 is set so that the less blade does not break as described above.

(Embodiment 2)
The second embodiment is an air conditioner configured by using the plate fin laminated heat exchanger according to the first embodiment.

FIG. 8 is a refrigeration cycle diagram of the air conditioner, and FIG. 9 is a schematic cross-sectional view showing the indoor unit of the air conditioner.

In FIGS. 8 and 9, the air conditioner is composed of an outdoor unit 51 and an indoor unit 52 connected to the outdoor unit 51. The outdoor unit 51 includes a compressor 53 for compressing the refrigerant, a four-way valve 54 for switching the refrigerant circuit during cooling and heating operation, an outdoor heat exchanger 55 for exchanging heat between the refrigerant and the outside air, a decompressor 56 for reducing the refrigerant, and an outdoor unit. A blower 59 is arranged. Further, the indoor unit 52 is provided with an indoor heat exchanger 57 for exchanging heat between the refrigerant and the indoor air, and an indoor blower 58. Then, 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 type refrigeration cycle.

In the refrigerant circuit according to the present embodiment, a refrigerant obtained by using tetrafluoropropene or trifluoropropene, difluoromethane or pentafluoroethane or tetrafluoroethane as a simple substance, or a mixture of two components or three components, respectively, is used.

The air conditioner having the above configuration 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 during the cooling operation. 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, it exchanges heat with the outside air to dissipate heat, becomes a high-pressure liquid refrigerant, and is sent to the decompressor 56. The decompressor 56 reduces the pressure to become a low-temperature 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 vaporizes, and becomes a low-temperature gas refrigerant. At this time, the indoor 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. As a result, 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 the indoor air to dissipate heat, and is cooled to become a high-pressure liquid refrigerant. At this time, the indoor air is heated to heat the room. After that, the refrigerant is sent to the compressor 56, decompressed in the compressor 56 to become a low-temperature low-pressure two-phase refrigerant, sent to the outdoor heat exchanger 55 to exchange heat with the outside air, evaporate and vaporize, and pass through the four-way valve 54. Then, it is returned to the compressor 53.

In the air conditioner configured as described above, by using the heat exchanger shown in the above embodiment for the outdoor heat exchanger 55 or the indoor heat exchanger 57, the heat exchanger is inexpensive and has pressure resistance. Since it is expensive, compact, and highly efficient, it can be an inexpensive, highly reliable, and highly energy-saving high-performance refrigeration system.

The plate fin laminated heat exchanger according to the present invention and the refrigeration system using the same have been described above using the above-described embodiment, but the present invention is not limited thereto. That is, the embodiments disclosed this time are exemplary and not restrictive in all respects, and the scope of the present invention is indicated by the claims, meaning and within the same meaning and scope as the claims. All changes are included.

The present invention is an inexpensive, highly reliable, compact and highly efficient plate fin laminated heat exchanger that achieves both end plate workability and plate fin pressure resistance, and high energy efficiency using the same. A refrigeration system can be provided. Therefore, it can be widely used in heat exchangers and various refrigeration equipment used for home and commercial air conditioners, and its industrial value is great.

1 Heat exchanger 2 Plate fin laminate 2a Plate fin 3a, 3b End plate 4 Tube A
5 Tube B
6a plate 6b plate 8 header flow path A
8a, 8c Opening 8b, 8d Ring-shaped concave groove 9 Fastening means (bolts and nuts)
10 Header flow path B
10a, 10c Opening 10b, 10d Ring-shaped concave groove 11 Communication flow path 11a, 11b Concave groove for communication flow path 12-minute flow path 12a, 12b Concave groove for branch flow path 14 Heat transfer flow path 14-1 Heat transfer flow path 14-2 Heat transfer return flow path 14a Concave groove for flow path formation 14b Concave groove for flow path formation 15 Protrusion 16 Insulation groove 17 Connecting part 18 Slit groove 19 Thin flat plate 20 Insulation slit groove 51 Outdoor unit 52 Indoor unit 53 Compressor 54 Four-way valve 55 Outdoor heat exchanger 56 Decompressor 57 Indoor heat exchanger 58 Indoor blower

Claims (4)

A plate fin laminate is formed by laminating a large number of plate fins having a plurality of heat transfer channels connected to a pair of inflow and outflow header channels, and end plates are joined and integrated on both end faces of the plate fin laminate. Plate fin laminated heat exchanger, the plate fins join plates having a plurality of flow path forming concave grooves to form a heat transfer flow path connected to a pair of header flow paths, and the heat transfer flow. The path forms a U-turn-shaped heat transfer flow path on each plate, and a pair of header flow paths connected to the path are collectively provided on one end side of the plate fin, and the U-turn-shaped heat transfer flow of the plate fin is provided. A slit-shaped heat insulating groove is formed between the forward flow path and the return flow path of the road, and the plate fins on both end faces of the plate fin laminate are formed on the plate having the flow path forming concave groove. A thin plate provided with a heat insulating slit groove facing the heat insulating groove of the plate fin is joined to form a heat transfer flow path, and the plate fins on both end faces are joined to the end plate via the thin flat plate. The end plate is provided with a slit groove at a position facing the heat insulating groove of the plate fin and the heat insulating slit groove of the thin plate, and the slit groove has a groove width wider than that of the heat insulating groove of the plate fin and the heat insulating slit groove of the thin plate. Widened plate fin laminated heat exchanger. The plate fin laminated heat exchanger according to claim 1, wherein the thin flat plate is formed by using the plate fin base plate of the plate fin. The plate fin laminated heat exchanger according to claim 1, wherein the thin flat plate is made of a plate material thinner than the end plate and thicker than the plate fins. A refrigeration system in which the heat exchanger constituting the refrigeration cycle is the heat exchanger according to any one of claims 1 to 3 .

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