JP2020165579A - Heat exchanger flow divider - Google Patents

Abstract

To solve a problem that a refrigerant unevenly flows to a plurality of flat tubes, as in an evaporation downstream-side header pipe in which the refrigerant of a small ratio of liquid refrigerant (gas rich) flows, energy lost by pressure loss and head difference is large as a flowing distance of the refrigerant from an inlet of a heat exchanger is long, that is, inertia force of the refrigerant rising in the header pipe is small as kinematic energy of the refrigerant is lowered, thus the liquid refrigerant hardly reaches an upper part of the header pipe, and deviates to a lower part of a heat exchange section.SOLUTION: A header pipe 3b has a partition plate 15 for defining a space 13 at connection side of the flat tubes 2 and a space 14 at a non-connection-side of the flat tubes 2 in a refrigerant outflow section 11 in which the refrigerant flows out to a plurality of flat tubes 2 in being functioned as an evaporator, the partition plate 15 has a plurality of communication holes 16a, 16b arranged in a vertical direction, and the communication hole 16a is constituted to be larger than an opening area of the communication hole 16b directly below the same.SELECTED DRAWING: Figure 2

Description

The present invention is composed of a pair of header pipes and a plurality of flat pipes having a plurality of refrigerant flow paths, and an air flowing between the plurality of flat pipes and a refrigerant flowing in the refrigerant flow paths of the flat pipes. It is related to a heat exchanger that exchanges heat with.

Conventionally, it has been composed of a pair of header pipes facing each other in the horizontal direction, a plurality of flat pipes having a plurality of refrigerant flow paths, and heat transfer fins provided between the flat pipes, and a plurality of flat pipes. A heat exchanger is known that exchanges heat between the air flowing between them and the refrigerant flowing in the refrigerant flow path of the flat pipe.

In this type of heat exchanger, a plurality of flat tubes are further grouped in each group, and each group constitutes a one-turn heat exchange section in which a refrigerant flows from one of the pair of header pipes to the other. Therefore, the upper and lower limits of the number of flat pipes that make up the heat exchange section of one turn are determined by the specified formula using the rated capacity of the air conditioner, the cross-sectional area of the refrigerant flow path of the flat pipe, and the hydraulic diameter. , A heat exchanger diversion device that can optimize the number of flat tubes in the heat exchange section and suppress the drift flow is disclosed. (See, for example, Patent Document 1).

FIG. 6 is a conventional heat exchanger described in Patent Document 1.

As shown in FIG. 6, the heat exchanger 100 is composed of a plurality of flat pipes 101 formed by a plurality of refrigerant flow paths and a pair of header pipes 102a and 102b connecting both ends of the flat pipes 101, respectively. The header pipes 102a and 102b are provided with partition plates 104a, 104b and 104c so as to divide the plurality of flat pipes 2 into a plurality of heat exchange sections 103a, 103b, 103c and 103d, and one header pipe 102a is provided with a refrigerant. The pipes 105a and 105b are connected.

The heat exchange sections 103a and 103b are separated by a partition plate 104a, the heat exchange sections 103b and 103c are separated by a partition plate 104b, and the heat exchange sections 103c and 103d are separated by a partition plate 104c.

The number of flat pipes 101 constituting each heat exchange section 103a, 103b, 103c, 103d is the heating rated capacity when the heat exchanger 100 is used as the outdoor unit of the air conditioner, and the refrigerant flow path of one flat pipe 101. It is within the upper limit number and the lower limit number obtained from the specified formula using the cross-sectional area and hydraulic diameter of.

When functioning as an evaporator, the refrigerant flowing from the refrigerant pipe 105b into one header pipe 102a passes through the heat exchange section 103d, flows to the other header pipe 102b, rises in the other header pipe 102b, and heat exchange section. It passes through 103c and flows out to one of the header pipes 102a.

Further, the refrigerant flowing through one header pipe 102a rises in one header pipe 102a, passes through the heat exchange section 103b, flows to the other header pipe 102b, rises in the other header pipe 102b, and heat exchanges. It passes through the section 103a and flows to one of the header pipes 102a.

Since the number of flat pipes 101 that do not cause drift when flowing from the header pipes 102a and 102b to the plurality of flat pipes 101 is set, the refrigerant can be evenly distributed to each flat pipe 101.

Japanese Unexamined Patent Publication No. 2014-48028

When functioning as an evaporator, the refrigerant evaporates each time it flows through each heat exchange section, and changes from a liquid state (liquid rich) to a gas state (gas rich) as it flows from the inlet to the outlet of the heat exchanger. Therefore, the state of the refrigerant that must be split into each heat exchange section differs. The flow state of the refrigerant differs depending on the refrigerant state, but the conventional configuration does not take into consideration the difference in the refrigerant state, so that it is insufficient for improving the diversion.

In particular, in the header pipe on the downstream side of evaporation where a low proportion of high-density liquid refrigerant (gas rich) flows, the flow distance of the refrigerant from the inlet of the heat exchanger becomes long, resulting in loss due to pressure loss and head difference. Since the energy generated is large and the kinetic energy decreases from the state of flowing into the heat exchanger, the inertial force rising in the header pipe is small, and it becomes difficult for the liquid refrigerant with high liquid density to reach the upper part, and the lower part of the heat exchange section. There was a problem that the refrigerant flowed unevenly to a plurality of flat tubes and the refrigerant flowed unevenly.

The present invention solves the above-mentioned conventional problems, and is a heat exchange composed of a plurality of flat pipes formed by a plurality of refrigerant flow paths and a pair of header pipes connecting both ends of the flat pipes. The purpose of the vessel is to allow the refrigerant to flow uniformly into a plurality of flat tubes.

In order to solve the above-mentioned conventional problems, the heat exchanger of the present invention is composed of a plurality of flat pipes having a plurality of refrigerant flow paths and a pair of header pipes connecting both ends of the flat pipes. In the heat exchanger, the header pipe includes a partition plate that divides a plurality of flat pipes into a plurality of heat exchange sections, and one of the first refrigerant pipes through which the refrigerant flows out when the heat exchanger functions as an evaporator. A second refrigerant pipe into which the refrigerant flows is provided above the header pipe and below the one header pipe, and the other header pipe is connected to the flat pipe in the refrigerant outflow section in which the refrigerant flows out to a plurality of flat pipes. It has a partition plate that separates the space from the space on the non-connecting side of the flat pipe, and the partition plate is provided with a plurality of communication holes arranged in the vertical direction above the intermediate position in the vertical direction of the refrigerant outflow section. Is provided so as to be larger than the opening area of the communication hole directly below.

As a result, the refrigerant that has flowed into the header pipe from the plurality of flat pipes flows into the non-connecting side space of the flat pipes in the refrigerant outflow section and rises. Especially in the header pipe on the downstream side of evaporation where the ratio of liquid refrigerant is small (gas rich) flows, the flow distance of the refrigerant from the second refrigerant pipe is long, the energy lost due to pressure loss and head difference is large, and the heat exchanger Since the kinetic energy decreases from the state of flowing into the header pipe, the inertial force of the refrigerant rising in the header pipe becomes smaller, and it is difficult for the high-density liquid refrigerant to reach the upper part of the header pipe, and it is lower than the upper communication hole. It becomes easy to flow from the communication hole into the connection side space of the flat pipe, but since the opening area of the lower communication hole is small, the flow path resistance becomes large and the refrigerant becomes difficult to flow.

Since the upper communication hole has a large opening area, the flow path resistance becomes small, and the refrigerant easily flows into the connection side space of the flat pipe.

In the heat exchanger of the present invention, especially when a refrigerant having a small proportion of liquid refrigerant (gas rich) flows, the refrigerant flowing into the header pipe from a plurality of flat pipes is difficult to reach when rising in the header pipe. Before flowing to the upper part of the pipe, it flows into the connection side space of the flat pipe only from the lower communication hole, and while suppressing the uneven flow of the refrigerant below the header pipe, the connection side space of the flat pipe from the upper communication hole. Since the refrigerant can easily flow to the upper flat pipe, the refrigerant can be uniformly flowed to the plurality of flat pipes.

Perspective view of the heat exchanger according to the first embodiment of the present invention. Sectional drawing of the xy plane of the header pipe of Embodiment 1 of this invention Xz front view showing the internal structure of the outdoor unit to which the heat exchanger is applied XY front view showing the internal structure of the outdoor unit to which the heat exchanger is applied Sectional drawing of the xy plane of the header pipe of Embodiment 2 of this invention Sectional view of the xy plane of a conventional heat exchanger

The first invention is in a heat exchanger composed of a plurality of flat pipes having a plurality of refrigerant flow paths and a pair of header pipes connecting both ends of the flat pipes, wherein the header pipe is a plurality of flat pipes. A partition plate for dividing the pipe into a plurality of heat exchange sections is provided, and when the heat exchanger functions as an evaporator, the first refrigerant pipe from which the refrigerant flows out is placed above one header pipe, and the second refrigerant flows into the pipe. The refrigerant pipe is provided below one header pipe, and the other header pipe has a flat pipe connecting side space and a flat pipe non-connecting side space in a refrigerant outflow section in which the refrigerant flows out to a plurality of flat pipes. The partition plate is provided with a plurality of communication holes arranged in the vertical direction above the intermediate position in the vertical direction of the refrigerant outflow section, and the communication holes are larger than the opening area of the communication holes directly below. The structure is provided so as to be used.

As a result, the refrigerant that has flowed into the header pipe from the plurality of flat pipes flows into the non-connecting side space of the flat pipes in the refrigerant outflow section and rises. Especially in the header pipe on the downstream side of evaporation where the ratio of liquid refrigerant is small (gas rich) flows, the flow distance of the refrigerant from the second refrigerant pipe is long, the energy lost due to pressure loss and head difference is large, and the heat exchanger Since the kinetic energy decreases from the state of flowing into the header pipe, the inertial force of the refrigerant rising in the header pipe becomes smaller, and it is difficult for the high-density liquid refrigerant to reach the upper part of the header pipe, and it is lower than the upper communication hole. It becomes easy to flow from the communication hole into the connection side space of the flat pipe, but since the opening area of the lower communication hole is small, the flow path resistance becomes large and the refrigerant becomes difficult to flow.

Since the upper communication hole has a large opening area, the flow path resistance becomes small, and the refrigerant easily flows into the connection side space of the flat pipe.

Therefore, especially when a refrigerant having a small proportion of liquid refrigerant (gas rich) flows, the refrigerant flowing into the header pipe from a plurality of flat pipes before flowing to the upper part of the header pipe which is difficult to reach when ascending in the header pipe. By flowing into the connection side space of the flat pipe only from the lower communication hole and suppressing the uneven flow of the refrigerant below the header pipe, it becomes easier to flow from the upper communication hole to the connection side space of the flat pipe. Since the refrigerant can flow to the upper flat pipe, the refrigerant can be uniformly flowed to the plurality of flat pipes.

The second invention has a structure in which a flow adjusting portion having an upward gradient is provided from the wall surface of the header pipe toward the upper end of the communication hole existing at the uppermost stage among the plurality of communication holes in the non-connection side space. To do.

As a result, a part of the refrigerant rising in the non-connecting side space of the flat pipe flows into the connecting side space of the flat pipe from the uppermost communication hole along the flow adjusting portion.

Therefore, especially during overload operation in which the amount of refrigerant circulation is large and the flow velocity of the refrigerant is high, the liquid refrigerant vigorously rises in the space on the non-connection side of the flat tube and collides with the upper surface of the space on the non-connection side, so that kinetic energy is generated. By reducing the number and suppressing the flow of the liquid refrigerant from the communication hole into the connection side space while falling, the liquid refrigerant that has risen in the non-connection side space can flow above the connection side space without dropping the kinetic energy. Since the refrigerant can flow to the upper flat pipe, the refrigerant can be uniformly flowed to the plurality of flat pipes.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to this embodiment.

(Embodiment 1)
FIG. 1 is a perspective view of the heat exchanger according to the first embodiment of the present invention. The x direction is the flow direction of the refrigerant flowing through the flow path of the flat pipe, the y direction is the axial direction of the header pipe, and the z direction is the air flow direction. Is. FIG. 2 is a cross-sectional view taken along the line AA of FIG. 1 (cross-sectional view taken along the xy plane of the heat exchanger according to the first embodiment of the present invention).

In FIGS. 1 and 2, the heat exchanger 1 includes a plurality of flat tubes 2 and a pair of header pipes 3a and 3b.

The plurality of flat pipes 2 are arranged in the horizontal direction (x direction) along the axial direction (y direction) of the header pipes 3a and 3b so as to be parallel to each other.

A plurality of fins 4 formed in a wavy shape that are continuous vertically are formed between the plurality of flat tubes 2, and the air flowing between the plurality of fins 4 and the air flowing through the plurality of flat tubes 2 flow. Heat exchange with the refrigerant.

As the refrigerant, for example, a mixed refrigerant containing R410A, R32 and R32 is used.

A plurality of refrigerant flow paths 5 provided in the flat pipe 2 communicate with the inside of the header pipes 3a and 3b.

The header pipes 3a and 3b are formed into a cylindrical shape by extrusion-molding a metal material such as aluminum.

A first refrigerant pipe 6 and a second refrigerant pipe 7 are connected to one header pipe 3a. The first refrigerant pipe 6 is connected above one header pipe 3a, and the second refrigerant pipe 7 is connected below one header pipe 3a, and is configured to function as an inlet or outlet of the refrigerant. ing.

In the header pipes 3a and 3b, a plurality of flat pipes 2 are provided in a plurality of heat exchange sections at positions between the first refrigerant pipe 6 and the second refrigerant pipe 7 in the height direction (y direction). Partition plates 9a, 9b, 9c for dividing into 8a, 8b, 8c, and 8d are provided.

The heat exchange sections 8a and 8b are separated by a partition plate 9a, the heat exchange sections 8b and 8c are separated by a partition plate 9b, and the heat exchange sections 8c and 8d are separated by a partition plate 9c, respectively.

In the space above the other header pipe 3b separated by the partition plate 9b, the refrigerant flows into the refrigerant inflow section 10 in which the refrigerant flows from the heat exchange section 8b and the heat exchange section 8a when functioning as an evaporator. The shaft of the other header pipe 3b that separates the dividing plate 12 that separates the outflowing refrigerant outflow section 11, the connecting side space 13 of the flat pipe 2 of the refrigerant outflow section 11, and the non-connecting side space 14 of the flat pipe 2. A partition plate 15 extending in the direction (y direction) is provided.

The dividing plate 12 is installed at the same height position in the y direction as the partition plate 9a provided in one of the header pipes 3a.

The partition plate 15 is provided with a plurality of communication holes 16a and 16b arranged in the vertical direction (y direction) above the intermediate position in the vertical direction (y direction), and the communication holes 16a are openings of the communication holes 16b directly below. It is configured to be larger than the area.

When the heat exchanger configured as described above functions as an evaporator, the refrigerant flowing from the second refrigerant pipe 7 into one header pipe 3a passes through the heat exchange section 8d in the + x direction and the other. Flows into the header pipe 3b of the above, rises in the other header pipe 3b in the + y direction, passes through the heat exchange section 8c in the −x direction, and flows out to one header pipe 3a.

Further, the refrigerant flowing through one header pipe 3a passes through the heat exchange section 8b in the + x direction and flows into the refrigerant inflow section 10 of the other header pipe 3b. The refrigerant in the refrigerant inflow section 10 goes toward the refrigerant outflow section 11 and rises in the non-connecting side space 14 in the + y direction. The raised refrigerant passes through the plurality of communication holes 16a and 16b provided in the partition plate 15, flows into the connection side space 13, passes through the heat exchange section 8a in the −x direction, and flows to one header pipe 3a.

Next, the use of the present embodiment will be described by taking as an example the case where the heat exchanger 1 of the present embodiment is used for the outdoor unit 20 of the air conditioner.

FIG. 3 is an xz plan view showing the internal structure of the outdoor unit 20 to which the heat exchanger 1 of the present embodiment is applied, and FIG. 4 is a plan view of the outdoor unit 20 to which the heat exchanger 1 of the present embodiment is applied. It is a xy plan view which shows the internal structure.

As shown in FIGS. 3 and 4, the outdoor unit 20 includes a compressor 21, a switching valve 22, an outdoor expansion valve 23, a blower 24, and a heat exchanger 1. The outdoor unit 20 and the indoor unit (not shown) are connected by a liquid pipe 25 and a gas pipe 26.

The header pipes 3a and 3b of the heat exchanger 1 are connected to the switching valve 22 via the first refrigerant pipe 6 and to the outdoor expansion valve 23 via the second refrigerant pipe 7, respectively.

First, when the cooling operation is performed, the heat exchanger 1 functions as a condenser.

The gas refrigerant sent from the compressor 21 of the outdoor unit 20 flows into one of the header pipes 3a from the first refrigerant pipe 6 via the switching valve 22. This gas refrigerant passes through the inside of one header pipe 3a on the connecting side of the first refrigerant pipe 6 separated by the partition plate 9a, flows into a plurality of refrigerant flow paths 5 in the plurality of flat pipes 2, and heats. It flows in the exchange section 8a in the horizontal direction (+ x direction, + z direction) and flows out to the other header pipe 3b. The outflowing refrigerant flows from the connection side space 13 through the plurality of communication holes 16a and 16b provided in the partition plate 15 into the non-connection side space 14, and flows in the other header pipe 3b in the vertical direction (−y direction). It descends to the heat exchange section 8b, flows in the horizontal direction (−z direction, −x direction), and flows out to one of the header pipes 3a.

Further, the refrigerant flowing out to one header pipe 3a descends in the one header pipe 3a in the vertical direction (−y direction), flows into the heat exchange section 8c, and flows in the horizontal direction (+ z direction, + x direction). , Outflows to the other header pipe 3b. The outflowing refrigerant descends in the other header pipe 3b in the vertical direction (−y direction), flows into the heat exchange section 8d, and flows in the horizontal direction (−z direction, −x direction).

The refrigerant dissipates heat and is condensed in the flat pipe 2 by exchanging heat with the air sent by the blower 24.

The condensed refrigerant flows out into the space of the header pipe 3a on the connection side of the second refrigerant pipe 7 separated by the partition plate 9c, passes through the outdoor expansion valve 23 and the liquid pipe 25 from the second refrigerant pipe 7, and is indoors. It is leaked to the machine.

The condensed refrigerant flowing into the indoor unit absorbs heat and evaporates by exchanging heat with air in an indoor heat exchanger (not shown). The evaporated refrigerant passes through the gas pipe 26 and circulates to the compressor 21 via the switching valve 22.

When performing a heating operation, the heat exchanger 1 functions as an evaporator.

The gas refrigerant sent from the compressor 21 of the outdoor unit 20 passes through the gas pipe 26 via the switching valve 22 and flows out to the indoor unit.

The gas refrigerant flowing into the indoor unit dissipates heat and condenses by exchanging heat with air in the indoor heat exchanger provided in the indoor unit.

The condensed refrigerant passes through the liquid pipe 25 and the outdoor expansion valve 23 to become a gas-liquid two-phase refrigerant, and is one of the connection sides of the second refrigerant pipe 7 separated by the partition plate 9c from the second refrigerant pipe 7. It passes through the inside of the header pipe 3a, flows into a plurality of refrigerant flow paths 5 in the plurality of flat pipes 2, flows in the heat exchange section 8d in the horizontal direction (+ x direction, + z direction), and flows out to the other header pipe 3b. .. The outflowing refrigerant rises in the other header pipe 3b in the vertical direction (+ y direction), flows into the heat exchange section 8c, flows in the horizontal direction (−z direction, −x direction), and goes to one header pipe 3a. leak.

Further, the refrigerant flowing out to one header pipe 3a rises in the one header pipe 3a in the vertical direction (+ y direction), flows into the heat exchange section 8b, and flows in the horizontal direction (+ x direction, + z direction). It flows into the refrigerant inflow section 10 in the other header pipe 3b.

A state in which the proportion of the liquid refrigerant that has flowed is small (gas rich) has a long flow distance of the refrigerant from the second refrigerant pipe 7, and a large amount of energy is lost due to pressure loss or head difference, and has flowed into the heat exchanger 1. As the kinetic energy decreases, the inertial force of the refrigerant rising in the other header pipe 3b becomes smaller, and it becomes difficult for the liquid refrigerant having a high density to reach the upper part of the header pipe.

The refrigerant easily flows from the communication hole 16b below the upper communication hole 16a into the connection side space 13 of the flat pipe 2, but the lower communication hole 16b has a small opening area, so that the flow path resistance becomes large. Since the refrigerant does not easily flow and the upper communication hole 16a has a large opening area, the flow path resistance becomes smaller, and the refrigerant flows from the upper communication hole 16a into the connection side space 13.

The refrigerant that has flowed into the connection side space 13 flows into the heat exchange section 8a and flows in the horizontal direction (−z direction, −x direction).

The refrigerant absorbs heat and evaporates in the flat pipe 2 by exchanging heat with the air sent by the blower 24.

The evaporated refrigerant flows out into the space of the header pipe 3a on the connection side of the first refrigerant pipe 6 separated by the partition plate 9a, and circulates from the first refrigerant pipe 6 to the compressor 21 via the switching valve 22. To do.

As described above, in the present embodiment, in the heat exchanger 1, a flat pipe 2 having a plurality of refrigerant flow paths 5 and a plurality of flat pipes 2 are installed in the horizontal direction, and both ends of the flat pipe 2 are respectively installed. A pair of header pipes 3a and 3b to be connected are provided, and a plurality of flat pipes 2 are connected in parallel to each other along the axial direction of the header pipes 3a and 3b.

The header pipes 3a and 3b include partition plates 9a, 9b, 9c for dividing the plurality of flat pipes 2 into a plurality of heat exchange sections 8a, 8b, 8c, 8d, and when the heat exchanger 1 functions as an evaporator, A first refrigerant pipe 6 through which the refrigerant flows is provided above one header pipe 3a, and a second refrigerant pipe 7 through which the refrigerant flows is provided below one header pipe 3b, and the refrigerant flows out in the other header pipe 3b. In the section 11, the partition plate 15 that separates the connecting side space 13 of the flat pipe 2 and the non-connecting side space 14 of the flat pipe 2 is provided, and the partition plate 15 is above the intermediate position in the vertical direction (y direction). , A plurality of communication holes 16a and 16b arranged in the vertical direction (y direction) are provided, and the communication holes 16a are configured to be larger than the opening area of the communication holes 16b directly below.

As a result, the refrigerant that has flowed into the other header pipe 3b from the plurality of flat pipes 2 flows into the non-connecting side space 14 of the flat pipes 2 in the refrigerant outflow section 11 and rises. In particular, in the other header pipe 3b on the downstream side of evaporation where a small proportion of liquid refrigerant (gas rich) flows, the flow distance of the refrigerant from the second refrigerant pipe 7 is long, and the energy lost due to pressure loss and head difference is large. As the kinetic energy decreases from the state of flowing into the heat exchanger, the inertial force of the refrigerant rising in the other header pipe 3b becomes smaller, and the high-density liquid refrigerant reaches above the other header pipe 3b. It is difficult, and it is easy to flow from the communication hole 16b below the upper communication hole 16a into the connection side space 13 of the flat pipe 2, but since the lower communication hole 16b has a small opening area, the flow path resistance becomes large. Refrigerant does not flow easily.

Since the upper communication hole 16a has a large opening area, the flow path resistance becomes small, and the refrigerant easily flows into the connection side space 13 of the flat pipe 2.

Therefore, especially when a refrigerant having a small proportion of liquid refrigerant (gas rich) flows, the refrigerant flowing into the other header pipe 3b from the plurality of flat pipes 2 communicates with the lower side when rising in the other header pipe 3b. It flows into the connection side space 13 of the flat pipe 2 only from the hole 16b, and flows from the upper communication hole 16a to the connection side space 13 of the flat pipe 2 while suppressing the uneven flow of the refrigerant below the other header pipe 3b. By facilitating the flow, the refrigerant can flow to the upper flat pipe 2, so that the refrigerant can flow uniformly to the plurality of flat pipes 2.

Further, when the refrigerant flows from the heat exchange section 8b to the heat exchange section 8a, the liquid refrigerant is preferentially flowed in the other header pipe 3b without connecting the connecting pipe as a separate member to the other header pipe 3b. Therefore, an increase in the internal volume of the other header pipe 3b can be suppressed, and the required amount of refrigerant can be reduced.

(Embodiment 2)
FIG. 5 is a cross-sectional view of the xy plane of the second embodiment of the present invention.

As shown in FIG. 5, in the non-connecting side space 14, an ascending slope is formed from the wall surface of the other header pipe 3b toward the upper end of the communication holes 16a existing at the uppermost stage among the plurality of communication holes 16a and 16b. A flow adjusting unit 17 is provided.

As a result, a part of the refrigerant rising in the non-connecting side space 14 of the flat pipe 2 flows into the connecting side space 13 of the flat pipe 2 from the uppermost communication hole 16a along the flow adjusting portion 17.

Therefore, especially during overload operation in which the amount of refrigerant circulating is large and the flow velocity of the refrigerant is high, the liquid refrigerant vigorously rises in the non-connecting side space 14 of the flat tube 2 and collides with the upper surface of the non-connecting side space 14. The kinetic energy is reduced, and the flow from the upper communication hole 16a into the connecting side space 13 while falling is suppressed, so that the kinetic energy of the liquid refrigerant that has risen in the non-connecting side space 14 is not reduced, and the connecting side space is not reduced. Since the refrigerant can flow above the 13 and the refrigerant can flow to the upper flat tube 2, the refrigerant can be uniformly flowed to the plurality of flat tubes 2.

Further, it is desirable that the wall surface connection position of the other header pipe 3b of the flow adjusting unit 17 is equal to or less than the vertical (y direction) intermediate position of the uppermost communication hole 16a.

As a result, the refrigerant rising in the non-connecting side space 14 of the flat pipe 2 comes into contact with the surface of the flow adjusting unit 17 more obliquely, and the liquid refrigerant is connected to the flat pipe 2 without losing the rising momentum. Since it flows into the side space 13, it can flow further above the connecting side space 13, the refrigerant can flow to the upper flat pipe 2, and the refrigerant can flow uniformly to the plurality of flat pipes 2.

Further, the plurality of communication holes 16a and 16b divide the number of the flat pipes 2 connected to the refrigerant outflow section 11 into equal parts by the number of the communication holes 16a and 16b, and among the plurality of flat pipes 2 separated, It is desirable to provide at least the height position of the flat tube 2 existing at the uppermost stage in the y direction. For example, when eight flat pipes 2 are connected to the refrigerant outflow section 11 and two communication holes 16a and 16b are provided, the upper communication hole 16a is the uppermost flat pipe among the eight flat pipes 2. The y-direction height position of 2 and the lower communication hole 16b include the y-direction height position of the fifth flat pipe 2 from the top among the eight flat pipes 2.

As a result, in the plurality of flat pipes 2 corresponding to the communication holes 16a and 16b, it is possible to secure a flow path through which the refrigerant flows to the flat pipe 2 existing at the position where the height in the y direction is highest, so that the refrigerant outflow section 11 It becomes easy to flow the refrigerant uniformly from the upper side to the lower side, and the refrigerant can flow uniformly through the plurality of flat pipes 2.

In the embodiment, one row of heat exchangers 1 is installed, but for example, two or more heat exchangers may be installed in the air flow direction (z direction), and two or more heat exchangers may be exchanged in the gravity direction (y direction). Needless to say, the same effect can be obtained even when the configuration in which the vessels 1 are stacked is used.

Further, in the embodiment, the plurality of fins 4 are formed in a wavy shape that is continuous vertically between the plurality of flat tubes 2, but are perpendicular to the plurality of flat tubes 2 so as to be parallel to each other. Needless to say, the same effect can be obtained even when the structure is formed in a plate shape so as to be inserted into.

Further, in the embodiment, the partition plate 15 is provided with two communication holes 16a and 16b arranged in the vertical direction (y direction), but it goes without saying that the same effect can be obtained even when two or more communication holes 16a and 16b are provided. No.

Further, in the embodiment, the flow adjusting portion 17 is formed of a flat surface, but it goes without saying that the same effect can be obtained even when the flow adjusting portion 17 is formed of a curved surface having a convex shape upward.

According to the present invention, in a heat exchanger using a flat tube, when a refrigerant having a high density and a small proportion of liquid refrigerant (gas rich) flows in the header pipe, the liquid refrigerant is biased downward and flows downward in the heat exchange section. It is a heat exchanger / refrigerant that can suppress this, and can be applied to applications such as refrigerators, air conditioners, and hot water supply / air conditioning combined devices.

1 Heat exchanger 2 Flat pipe 3a, 3b Header pipe 4 Fin 5 Refrigerant flow path 6 First refrigerant pipe 7 Second refrigerant pipe 8a, 8b, 8c, 8d Heat exchange section 9a, 9b, 9c Partition plate 10 Refrigerant inflow Section 11 Refrigerant outflow section 12 Dividing plate 13 Connection side space 14 Non-connection side space 15 Partition plate 16a, 16b Communication hole 17 Flow adjustment unit 20 Outdoor unit 21 Compressor 22 Switching valve 23 Outdoor expansion valve 24 Blower 25 Liquid pipe 26 Gas pipe 100 Heat exchanger 101 Flat pipe 102a, 102b Header pipe 103a, 103b, 103c, 103d Heat exchange section 104a, 104b, 104c Partition plate 105a, 105b Refrigerant piping

Claims (2)

In a heat exchanger composed of a plurality of flat pipes having a plurality of refrigerant flow paths and a pair of header pipes connecting both ends of the flat pipes, the header pipe includes a plurality of the flat pipes. When the heat exchanger functions as an evaporator, the first refrigerant pipe from which the refrigerant flows is provided above the one header pipe, and the second refrigerant flows into the heat exchange section. A refrigerant pipe is provided below one of the header pipes, and the other header pipe is not connected to the connection side space of the flat pipes in the refrigerant outflow section where the refrigerant flows out to the plurality of flat pipes. The partition plate has a partition plate separating the side space, and the partition plate has a plurality of communication holes arranged in the vertical direction above the intermediate position in the vertical direction of the refrigerant outflow section, and the communication holes are directly below the above. A heat exchanger diversion device characterized by being larger than the opening area of the communication hole. In the non-connection side space, a flow adjusting portion having an upward gradient is provided from the wall surface of the header pipe toward the upper end of the communication hole existing at the uppermost stage among the plurality of communication holes. The heat exchanger shunt according to claim 1.

Images