JP4983878B2 - Heat exchanger, refrigerator equipped with this heat exchanger, and air conditioner - Google Patents

Description

  The present invention relates to a heat exchanger widely used for an evaporator, a condenser, and the like such as a refrigeration apparatus and an air conditioner.

  In heat exchangers that make up conventional refrigerators and air conditioners, piping that forms the refrigerant flow path is a flat tube, and corrugated aluminum fins are brazed to the outside of the flat tube, and both ends of a plurality of flat tubes Some have a header connected to the part (see, for example, Patent Document 1). In addition, there is an evaporator that achieves stable and constant heat conduction by integrating the fin and the tube (for example, see Patent Document 2).

JP 2006-200881 (page 8, line 7, page 16, FIG. 1) JP-A-63-150585 (second page, upper left row, 10th line, page 4, Fig. 1)

  However, in the configuration of the heat exchanger described in Patent Document 1, the connection between the flat tube and the corrugated aluminum fin is performed by brazing in a high-temperature furnace. Contact thermal resistance exists between tube-shaped aluminum fins. Moreover, since the heating process of a heat exchanger is needed, manufacturing cost rises. Furthermore, since the headers are connected to both end portions of the plurality of flat tubes, the heat distribution performance may not be obtained due to the inability to evenly distribute the refrigerant flow paths of all the flat tubes.

  Further, the configuration of the heat exchanger described in Patent Document 2 is formed in a substantially H-shaped cross section, and there is a problem that the contact area between the fin and the refrigerant passage is small and heat exchange is not efficient. Further, when a plurality of refrigerant passages are provided in order to increase the heat transfer area in the pipe, the refrigerant passages are added in a direction perpendicular to the air flow. However, if the area of the refrigerant passage is constant, the thickness dimension increases. The airflow resistance increases, and when the thickness dimension is constant, the area of the refrigerant passage is reduced and the refrigerant resistance is increased. In addition, in any case, there is a problem that a refrigerant passage that does not come into contact with the fins is formed, and the heat exchange efficiency cannot be improved after all.

  The present invention has been made to solve the above-described problems. The contact area between the refrigerant passage and the fin is increased, the shape of the refrigerant passage is appropriate, and the heat exchange efficiency between the air and the refrigerant is improved. An object is to provide an enhanced heat exchanger and a refrigerator or an air conditioner using the heat exchanger.

The heat exchanger according to the present invention has a flat surface, and is bent in a meandering manner in a plane parallel to the flat surface, whereby the heat transfer tube traversing the airflow flowing along the flat surface a plurality of times, and the heat transfer tube A plurality of refrigerant passages formed inside the heat transfer tube along the flat surface of the heat pipe, and a plurality of fins formed by cutting the flat surface of the heat transfer tube , the plurality of refrigerant passages being meandering The upstream side and the downstream side are interchanged with respect to the airflow at the bend portion.

  ADVANTAGE OF THE INVENTION According to this invention, the heat exchange efficiency with the air and refrigerant | coolant in a heat exchanger can be improved. Moreover, heat exchange efficiency improves and it is effective by using this heat exchanger for a refrigerator or an air conditioner.

1 is an external view of a heat exchanger according to Embodiment 1. FIG. (A) is a side view of the heat exchanger tube concerning Embodiment 1, (b) is a sectional view similarly. 2 is an external view of a heat transfer tube according to Embodiment 1. FIG. 6 is an external view of a heat transfer tube according to Embodiment 2. FIG. 6 is an external view of a main part of a heat exchanger according to Embodiment 2. FIG. 6 is an external view of a heat transfer tube according to Embodiment 3. FIG. 6 is an external view of a heat exchanger according to Embodiment 4. FIG. It is a figure which shows the relationship between the number (number of holes) of the refrigerant path which concerns on Embodiment 5, and a heat exchange rate. FIG. 10 is an enlarged sectional view of a heat transfer tube according to a sixth embodiment. It is a figure which shows the relationship between the ratio of the protrusion height and outer diameter of a heat exchanger tube, and a heat exchange rate. It is a figure which shows the relationship between the number of protrusions of a heat exchanger tube, and a heat exchange rate. FIG. 12 is a configuration diagram of an air conditioner according to Embodiment 9.

Embodiment 1 FIG.
FIG. 1 is an external view of a heat exchanger according to Embodiment 1 of the present invention. In FIG. 1, the heat exchanger 1 includes a flat heat transfer tube 11 and a plurality of heat exchanger fins 10 provided on a flat surface of the heat transfer tube 11. The heat transfer tube 11 is bent in a meandering manner in a plane parallel to the flat surface of the heat transfer tube 11 at the bent portion 13, so that the refrigerant flowing inside the heat transfer tube 11 flows against the airflow flowing along the flat surface. Are configured to cross multiple times. The airflow flows, for example, from the lower side of the figure to the upper side of the figure, and the fins 10 are provided so as to be parallel to the airflow and are formed so as not to be resistant to the airflow. Note that the fin 10 is formed on the heat transfer tube 11 other than the bent portion 13.

  2A is a side view of the heat transfer tube 11 according to the first embodiment, and FIG. 2B is a cross-sectional view of the heat transfer tube according to the first embodiment. The heat transfer tube 11 has a rectangular flat shape, and a fin 10 is cut perpendicularly and parallel to the longitudinal direction of the heat transfer tube 11 on one flat surface of the heat transfer tube 11 with a predetermined interval. woken up. The fin 10 is integrally formed by cutting and raising the material surface of the heat transfer tube 11 at a predetermined thickness until it is almost vertical. In addition, a refrigerant passage 16 through which the refrigerant flows is provided inside the heat transfer tube 11, and the refrigerant is configured to flow in a direction orthogonal to the surface of the fin 10. The refrigerant passage 16 is formed integrally with the heat transfer tube 11 by, for example, making a hole in the metal forming the heat transfer tube 11. In addition, the refrigerant passage 16 is formed along the flat surface of the heat transfer tube 11 and is configured so that resistance to the airflow does not increase.

  FIG. 3 is an external view of the heat transfer tube according to the first embodiment, and shows the heat transfer tube in a state before bending when the bent portion 13 is one place. In FIG. 3, fins 10 are provided by cutting and raising on a flat surface in a range corresponding to approximately ½ of the entire length of the heat transfer tube 11, and a remaining bent portion 13 having a predetermined interval as a bending allowance is separated. The fin 10 is cut and raised on a flat surface of 1/2, and the fin 10 and the heat transfer tube 11 are integrally formed. Although FIG. 3 shows an example in which the bent portion 13 is one place, the bent portion 13 can be formed in the same manner when there are two or more bent portions 13. The heat exchanger 1 is formed by bending such a heat transfer tube horizontally.

  The heat transfer tube 11 is made of a metal material having a high thermal conductivity such as copper, a copper alloy, aluminum, an aluminum alloy, or titanium. The same applies to other embodiments. Further, the number of refrigerant passages 16 is not limited to two.

  In addition, the shape of the fin 10 is not limited to a plate shape, and may be an appropriate fin shape such as a strip shape or a needle shape.

Next, the operation will be described.
The heat transfer tube 11 becomes a part of the refrigerant circuit in the refrigeration cycle apparatus. Then, the refrigerant enters the heat transfer tube 11 from the lower right of FIG. 1 and flows through the tube, while the airflow flows upward from the lower side of the drawing, and the heat transfer tube 11 and the air intersect each other. A part of the heat of the refrigerant flowing inside the heat transfer tube 11 is transferred to the fin 10, and heat exchange is performed between the air flowing outside the heat transfer tube 11.

  At this time, as described above, the fin 10 and the refrigerant passage 16 are configured to reduce the air resistance with respect to the flow of the airflow, so that the airflow efficiently passes through the heat exchanger 1. Further, since the heat transfer tube 11 and the fin 10 are integrally formed, the contact thermal resistance is zero, and the heat of the refrigerant flowing in the heat transfer tube 11 is efficiently transmitted to the fin 10. Further, since the fin 10 has a large heat transfer area as a contact surface with air, the heat transferred to the fin 10 is efficiently exchanged with air.

  The refrigerant flowing through the heat transfer tube 11 passes through the bent portion 13 of the heat transfer tube 11 and flows through the heat transfer tube 11. After passing through the bent portion 13, the refrigerant passage 16 is reversed with respect to the airflow. That is, the refrigerant passage 16 that has flowed upstream with respect to the airflow passes through the bent portion 13. Therefore, the refrigerant flowing through any refrigerant passage 16 can be heat-exchanged evenly, so that the efficiency of the heat exchanger is increased.

  Moreover, since the heat exchanger 1 is formed by bending the heat transfer tube 11, the number of brazing points is reduced, and the processing cost can be reduced and the reliability can be improved.

  As described above, according to the first embodiment, there is an effect that a heat exchanger with low air resistance against airflow and high heat exchange efficiency can be obtained.

Embodiment 2. FIG.
FIG. 4 is an external view of the heat transfer tube according to the second embodiment, and fins are formed so that the fin pitch is reduced with the bent portion 13 interposed therebetween. That is, in FIG. 4, it is formed so that the fin pitch on the right side is smaller than the fin pitch on the left side of the bent portion 13. Although FIG. 4 shows an example in which the bent portion 13 is one, even if there are a plurality of bent portions 13, they can be formed in the same manner.

  FIG. 5 is an external view of the main part of the heat exchanger 1 formed by bending the heat transfer tube shown in FIG. 4, and the bent portion 13 is omitted. In FIG. 5, it arrange | positions so that the pitch of the fin 10 formed in the upper surface of the heat exchanger tube 11 located in the upstream of an airflow may become large compared with the downstream of an airflow.

  In general, a smaller pitch of the fins 10 results in more fins 10 being formed and a larger heat transfer area, so heat exchange efficiency is improved. However, if the pitch of the fins 10 on the upstream side is small, dust carried by the air There is a possibility that the air passage becomes narrow and the air resistance increases due to adhesion to the fin 10 or water vapor contained in the air becoming frost and adhering to the fin 10.

  Therefore, according to the second embodiment, the fin pitch is formed so as to be gradually decreased with the bent portion interposed therebetween, and the heat transfer tube having a large fin pitch is arranged on the upstream side of the airflow, thereby preventing adhesion of dust, frost, and the like. Since the accompanying narrowing of the air passage can be reduced, an increase in air resistance can be suppressed.

Embodiment 3 FIG.
In the embodiment described above, the fin 10 is formed by cutting and raising one side of the flat surface of the heat transfer tube 11, but in the third embodiment, the fin 10 is formed by cutting and raising the fin 10 on both sides of the flat surface.

  FIG. 6 is an external view of the heat transfer tube 11 according to the third embodiment, and shows the heat transfer tube 11 in a state before bending when the bent portion 13 is one place. In FIG. 6, a bent portion having a predetermined interval as a bending margin for bending horizontally by cutting and raising fins 10 on both the upper and lower surfaces of a flat surface in a range approximately ½ of the length of the heat transfer tube 11. The fins 10 are similarly cut and raised in the remaining ½ range with the gap 13 therebetween, and the fins 10 and the heat transfer tubes 11 are integrally formed. The heat exchanger 1 is formed by horizontally bending such a heat transfer tube. And when a refrigerant | coolant flows through the inside of this heat exchanger 1, heat exchange with a refrigerant | coolant and air is performed.

  According to the third embodiment, since the fins 10 are provided on both surfaces, the heat transfer area serving as a contact surface with the air is widened, so that the efficiency of heat exchange between the refrigerant and the air can be increased. There is.

Embodiment 4 FIG.
FIG. 7 is an external view of a heat exchanger according to the fourth embodiment. A plurality of heat exchangers according to the first embodiment are arranged so as to be superposed in the vertical direction on the flat surface, and one end of both refrigerant passages 16 in the upper right part of the figure is connected by a return bend pipe 12. . There is no partition inside the return bend pipe 12, and it has a structure having one passage. The return bend pipe 12 is made of a metal material such as copper or copper alloy, aluminum or aluminum alloy, for example.

  The refrigerant that has entered the heat transfer tube 11 from the inlet of the refrigerant passage 16 proceeds through the heat transfer tube 11 while exchanging heat with air. Since the return bend pipe 12 has a structure having one passage, the refrigerant that has entered the return bend pipe 12 from the refrigerant passage 16 is mixed in the return bend pipe 12 and the gas phase and liquid in each refrigerant passage 16 are mixed. The mass ratio with the phase becomes the same. As a result, the heat exchanging ability of the refrigerant flowing through each refrigerant passage 16 becomes equal, and the efficiency of the heat exchanger can be increased. The mixed refrigerant flows through the heat transfer tube 11 at the other stage, further exchanges heat with air, and is discharged from the refrigerant outlet.

  According to the fourth embodiment, the refrigerant flowing through each refrigerant passage 16 is mixed by the return bend pipe 12, and the heat exchange capacity of the refrigerant is equalized. Therefore, the efficiency of the heat exchanger can be further improved. .

  In the present embodiment, an example in which the fins 10 are cut and raised at an equal pitch on one side of the heat transfer tube 11 is described. However, as in the second embodiment, the fin pitch of the upstream heat transfer tube 11 is described. The fins 10 may be cut and raised on both sides as in the third embodiment.

Embodiment 5 FIG.
In the fifth embodiment, 2 to 5 refrigerant passages 16 are arranged side by side in a flat heat transfer tube 11.

  FIG. 8 is a diagram showing the relationship between the number of refrigerant passages formed in the heat transfer tube 11 and the heat exchange rate. As shown in FIG. 8, the heat exchange rate when the number of the refrigerant passages 16 is 2 to 5 is larger than that when the number of the refrigerant passages 16 is 1 or 6 or more. It can be seen that it is desirable to provide five refrigerant passages 16.

  This is because if the number of refrigerant passages is one, the heat transfer area in the tube is reduced, and the heat transfer performance in the tube is reduced. This is thought to be due to an increase in. In addition, when the width of the heat transfer tube 11 is constant, it is considered that providing more than five refrigerant passages 16 reduces the inner diameter of the refrigerant passage 16 and increases the pressure loss inside the tube.

  Note that the shape of the refrigerant passage 16 is not limited to a quadrangular shape, and may be an appropriate cross-sectional shape such as an elliptical shape or a circular shape.

  According to the fifth embodiment, it is possible to further improve the efficiency of the heat exchange rate by forming two to five refrigerant passages 16 in the heat transfer tube 11 having a flat shape.

Embodiment 6 FIG.
FIG. 9 shows a cross-sectional view of the heat transfer tube 11 in the sixth embodiment. In FIG. 9, although the number of the refrigerant passages 16 is two, it is not limited to this. A plurality of protrusions 15 that are continuous in the refrigerant flow direction are integrally provided in the refrigerant passage 16 so that the contact area between the refrigerant and the heat transfer tube 11 is increased. Further, in the figure, h indicates the protrusion height of the protrusion, and D indicates the width of the heat transfer tube 11 in the flat direction.

  Further, the cross-sectional shape of the protrusion 15 is not limited to a quadrangular shape, and may be an appropriate cross-sectional shape such as a triangular shape, a trapezoidal shape, or a semicircular shape.

  According to the sixth embodiment, since the heat transfer area between the refrigerant and the heat transfer tube is increased by the protrusions 15, there is an effect that the heat exchange efficiency can be further increased.

Embodiment 7 FIG.
In the seventh embodiment, the protrusion 15 is formed so that the ratio (h / D) of the height h of the protrusion 15 to the width D in the flat direction of the heat transfer tube 11 is about 0.02 to 0.05. ing.

  FIG. 10 is a diagram showing the relationship between the ratio (h / D) of the height h of the protrusion 15 to the width D in the flat direction and the heat exchange rate. As shown in FIG. 10, when h / D is increased, the refrigerant contact area in the pipe is increased, so that the heat exchange rate is also increased. However, when h / D exceeds 0.05, the amount of increase in pressure loss is greater than the amount of increase in heat exchange rate, and as a result, the heat exchange rate decreases.

  According to the seventh embodiment, by forming the protrusion 15 so that the ratio of the height h of the protrusion 15 to the width D in the flat direction of the heat transfer tube 11 is about 0.02 to 0.05, There is an effect that the exchange rate can be increased.

Embodiment 8 FIG.
In the eighth embodiment, the ridges 15 are formed so that the number n of the ridges 15 is about 2 to 5.

  FIG. 11 is a diagram showing the relationship between the number n of the protrusions 15 and the heat exchange rate. As shown in FIG. 11, when the number n of the protrusions 15 is increased, the refrigerant contact area in the pipe is increased, so that the heat transfer coefficient is also increased. However, when the number n of the protrusions 15 exceeds 5, the amount of increase in pressure loss is greater than the amount of increase in heat transfer coefficient, and as a result, the heat exchange rate decreases.

  According to the eighth embodiment, there is an effect that the heat exchange rate can be increased by forming the protrusions 15 so that the number n of the protrusions 15 is about 2 to 5.

Embodiment 9 FIG.
FIG. 12 is a configuration diagram of an air-conditioning apparatus according to Embodiment 9 of the present invention.
In the present embodiment, an air conditioner will be described as an example of a refrigeration cycle apparatus. The air conditioner of FIG. 12 includes a heat source side unit (outdoor unit) 100 and a load side unit (indoor unit) 200, which are connected by a refrigerant pipe to constitute a refrigerant circuit and circulate the refrigerant.

  Among the refrigerant pipes, a pipe through which a gaseous refrigerant (gas refrigerant) flows is referred to as a gas pipe 300, and a pipe through which a liquid refrigerant (liquid refrigerant, which may be a gas-liquid two-phase refrigerant) flows is referred to as a liquid pipe 400. Here, as the refrigerant, for example, an HC single refrigerant or a mixed refrigerant containing HC, or any refrigerant such as R32, R410A, R407C, carbon dioxide, or the like is used.

  In the heat source side unit 100, a compressor 101, an oil separator 102, a four-way valve 103, a heat source side heat exchanger 104, a heat source side expansion device (expansion valve) 107, an accumulator 106, an inter-refrigerant heat exchanger 108, and a bypass expansion device 109. Are connected by refrigerant piping as shown in FIG. The heat source side heat exchanger 104 is provided with a heat source side fan 105. In the heat source side unit 100, a heat source side control device 110 for controlling the compressor 101, the four-way valve 103, and the heat source side fan 105 is provided.

  The compressor 101 has an electric motor. The compressor 101 sucks and compresses the refrigerant that has passed through the accumulator 106 and converts it into a high-temperature and high-pressure gas state to flow through the refrigerant pipe. The compressor 101 can change the capacity | capacitance (the amount which sends out the refrigerant | coolant per unit time) finely by changing an operating frequency arbitrarily with an inverter circuit (not shown).

  The oil separator 102 separates lubricating oil discharged from the compressor 101 mixed with refrigerant. The separated lubricating oil is returned to the compressor 101. The four-way valve 103 switches the refrigerant flow between the cooling operation and the heating operation based on an instruction from the heat source side control device 110.

  The heat source side heat exchanger 104 is configured using the heat exchanger 1 described in the first to eighth embodiments, and performs heat exchange between the refrigerant and air (outdoor air). For example, during the heating operation, it functions as an evaporator, performs heat exchange between the low-pressure refrigerant that has flowed in through the heat source side expansion device 107 and air, and evaporates and vaporizes the refrigerant. Further, during the cooling operation, it functions as a condenser and performs heat exchange between the refrigerant compressed in the compressor 101 flowing in from the four-way valve 103 side and air, thereby condensing and liquefying the refrigerant.

  Further, the heat source side heat exchanger 104 is provided with a heat source side fan 105 in order to efficiently exchange heat between the refrigerant and the air. The heat source side fan 105 may also have an inverter circuit (not shown), and the fan motor operating frequency may be arbitrarily changed to finely change the rotation speed of the fan.

  The inter-refrigerant heat exchanger 108 exchanges heat between the refrigerant flowing in the main flow path of the refrigerant circuit and the refrigerant branched from the flow path and adjusted in flow rate by the bypass expansion device 109 (expansion valve). . In particular, when it is necessary to supercool the refrigerant during the cooling operation, the refrigerant is supercooled and supplied to the load side unit 200. The inter-refrigerant heat exchanger 108 is also configured using the heat exchanger 1 described in the first to eighth embodiments.

  The liquid flowing through the bypass throttle device 109 is returned to the accumulator 106. The accumulator 106 is means for storing, for example, liquid excess refrigerant.

  The heat source side control device 110 is composed of, for example, a microcomputer. It is possible to communicate with the load-side control device 204 in a wired or wireless manner. For example, based on data related to detection by various detection means (sensors) in the air conditioner, the operation frequency control of the compressor 101 by inverter circuit control, etc. Then, each means related to the air conditioner is controlled to control the operation of the entire air conditioner.

  On the other hand, the load side unit 200 includes a load side heat exchanger 201, a load side expansion device (expansion valve) 202, a load side fan 203, and a load side control device 204.

  The load-side heat exchanger 201 is also configured using the heat exchanger 1 described in Embodiments 1 to 8, and performs heat exchange between the refrigerant and the air in the space to be air-conditioned. For example, during heating operation, it functions as a condenser, performs heat exchange between the refrigerant flowing in from the gas pipe 300 and air, condenses and liquefies the refrigerant (or gas-liquid two-phase), and moves to the liquid pipe 400 side. Spill. On the other hand, during the cooling operation, it functions as an evaporator, performs heat exchange between the refrigerant and the air whose pressure is reduced by the load-side throttle device 202, causes the refrigerant to take heat of the air, evaporates it, and vaporizes it. It flows out to the piping 300 side.

  In addition, the load side unit 200 is provided with a load side fan 203 for adjusting the flow of air for heat exchange. The operating speed of the load-side fan 203 is determined by, for example, user settings. The load side expansion device 202 is provided to adjust the pressure of the refrigerant in the load side heat exchanger 201 by changing the opening degree.

  The load-side control device 204 is also composed of a microcomputer or the like, and can communicate with, for example, the heat source-side control device 110 in a wired or wireless manner. Based on an instruction from the heat source side control device 110 and an instruction from a resident or the like, for example, each device (means) of the load side unit 200 is controlled such that the room has a predetermined temperature. Further, a signal including data related to detection by the detection means provided in the load side unit 200 is transmitted.

  Next, the operation of the air conditioner will be described.

  First, basic refrigerant circulation in the refrigerant circuit during cooling operation will be described. Due to the driving operation of the compressor 101, the high-temperature, high-pressure gas (gas) refrigerant discharged from the compressor 101 is condensed by passing through the heat source side heat exchanger 104 from the four-way valve 103 and becomes a liquid refrigerant. The side unit 100 flows out.

  The refrigerant flowing into the load side unit 200 through the liquid pipe 400 evaporates as the low temperature and low pressure liquid refrigerant whose pressure is adjusted by adjusting the opening degree of the load side expansion device 202 passes through the load side heat exchanger 201. leak. Then, it flows into the heat source side unit 100 through the gas pipe 300, is sucked into the compressor 101 through the four-way valve 103 and the accumulator 106, and is circulated by being pressurized and discharged again.

  Next, basic refrigerant circulation in the refrigerant circuit during heating operation will be described. Due to the driving operation of the compressor 101, the high-temperature, high-pressure gas (gas) refrigerant discharged from the compressor 101 flows into the load side unit 200 from the four-way valve 103 through the gas pipe 300.

In the load-side unit 200, the pressure is adjusted by adjusting the opening degree of the load-side expansion device 202, and condensed by passing through the load-side heat exchanger 201 to become an intermediate-pressure liquid or a gas-liquid two-phase refrigerant. And flows out of the load side unit 200. The refrigerant flowing into the heat source side unit 100 through the liquid pipe 400 is pressure-adjusted by adjusting the opening degree of the heat source side expansion device 107, evaporates by passing through the heat source side heat exchanger 104, and becomes a gas refrigerant. Then, the refrigerant is sucked into the compressor 101 through the four-way valve 103 and the accumulator 106, and circulated by being pressurized and discharged as described above.

  As described above, according to the air conditioning apparatus of the ninth embodiment, heat exchange is performed on the heat source side heat exchanger 104 of the heat source side unit 100, the inter-refrigerant heat exchanger 108, and the load side heat exchanger 201 of the load side unit 200. Since the high-efficiency heat exchangers 1 of the first to eighth embodiments are used as an evaporator and a condenser, COP (Coefficient of Performance: energy consumption efficiency, coefficient of performance) and the like can be improved, thereby saving energy. There is an effect that it can be achieved.

  Further, by using any one of refrigerants such as HC single refrigerant or HC, or R32, R410A, R407C, carbon dioxide, etc. as the refrigerant, the heat transfer capability can be increased and the heat exchange rate can be increased. There is an effect that can be done.

  The heat exchanger according to the present invention is not limited to an air conditioner, and other refrigeration cycle apparatuses having a heat exchanger that constitutes a refrigerant circuit such as a refrigeration apparatus, a heat pump apparatus, and the like, and has an evaporator and a condenser. It can also be applied to.

1 heat exchanger 10 fin 11 heat transfer tube 12 return bend tube 13 bent portion 15 ridge 16 refrigerant passage 100 heat source side unit 101 compressor 102 oil separator 103 four-way valve 104 heat source side heat exchanger 105 heat source side fan 106 accumulator 107 heat source Side expansion device 108 Inter-refrigerant heat exchanger 109 Bypass expansion device 110 Heat source side control device 200 Load side unit 201 Load side heat exchanger 202 Load side expansion device 203 Load side fan 204 Load side control device 300 Gas piping 400 Liquid piping

Claims (11)

A heat transfer tube having a flat surface and traversing the airflow flowing along the flat surface a plurality of times by being meandered in a plane parallel to the flat surface;
A plurality of refrigerant passages formed inside the heat transfer tube along the flat surface of the heat transfer tube ;
A plurality of fins formed by cutting and raising the flat surface of the heat transfer tube ,
The heat exchanger according to claim 1, wherein the plurality of refrigerant passages are switched between the upstream side and the downstream side with respect to the air flow with a meandering bent portion as a boundary . Fins formed on the heat transfer tube is formed in addition to the bent portions of the heat transfer tubes, fin pitch of the fins, the heat exchanger according to claim 1 which is formed so as to gradually become smaller across the bent portion . The fin heat exchanger according to any one of claims 1 to 2 are formed on both flat surfaces of the heat transfer tube. A heat formed by arranging a plurality of heat exchangers according to any one of claims 1 to 3 in a direction perpendicular to the flat surface and connecting adjacent heat exchangers with a return bend pipe. Exchanger. The heat exchanger according to any one of claims 1 to 4 , wherein the number of the refrigerant passages is 2 to 5. The heat exchanger according to any one of claims 1 to 5 , wherein a protrusion that is continuous in a direction in which the refrigerant flows is provided inside the refrigerant passage. The heat exchanger according to claim 6 , wherein a ratio of a height of the protrusion to a flat width of the heat transfer tube is 0.02 to 0.05. The heat exchanger according to claim 6 or 7 , wherein the number of the protrusions is 2 to 5. A pipe for connecting a compressor for compressing the refrigerant, a condenser for condensing the refrigerant by heat exchange, an expansion means for depressurizing the condensed refrigerant, and an evaporator for evaporating the decompressed refrigerant by heat exchange A refrigeration cycle apparatus that constitutes a refrigerant circuit for connecting and circulating the refrigerant,
A refrigeration cycle apparatus using the heat exchanger according to any one of claims 1 to 8 for one or both of the condenser and the evaporator. The refrigeration cycle apparatus according to claim 9 , wherein the refrigerant is one of HC single refrigerant, a mixed refrigerant containing HC, R32, R410A, R407C, and carbon dioxide. Refrigerator or air conditioner using the refrigerating cycle apparatus according to any one of claims 9 or 10.

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