JP2016070648A - Refrigerant distributor, and refrigeration cycle device including refrigerant distributor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerant distributor and a refrigeration cycle device using the same, capable of stably distributing a refrigerant to refrigerant pipes while suppressing increase of costs under a flow rate condition from a rated operating condition to an operating condition of low rotation.SOLUTION: A refrigerant distributor 21 includes an inlet pipe 31, a header pipe 30 connected to the inlet pipe, and a plurality of refrigerant pipes 32 connected to one end side 43 of the header pipe at a vertical lower part with respect to the inlet pipe, and distributes the refrigerant flowing into the header pipe from the inlet pipe to the plurality of refrigerant pipes. The header pipe is disposed in a state that a vertical upper side of the header pipe is inclined to one end side to which the refrigerant pipes are connected.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a refrigerant distributor that distributes refrigerant to a plurality of refrigerant pipes and a refrigeration cycle apparatus including the refrigerant distributor.

  In general, a refrigeration cycle apparatus such as an air conditioner or a heat pump water heater has a refrigerant circuit in which a compressor, a throttle device such as an electric valve, a condenser and an evaporator are connected by piping. In the refrigeration cycle of the refrigeration cycle apparatus, the refrigerant circulating in the refrigerant circuit repeatedly absorbs or releases heat with respect to air, water, and the like that are heat exchange targets in the heat exchanger (condenser and evaporator).

  For example, a heat exchanger of an air conditioner indoor unit or outdoor unit joins a plurality of refrigerant tubes to fins that are air-side heat transfer surfaces of the heat exchanger, so that the refrigerant in the refrigerant tube and the air Efficient heat transfer. In this structure, it is necessary to distribute the refrigerant to each of a plurality of refrigerant tubes provided in parallel in the heat exchanger of the indoor unit or the outdoor unit. The refrigerant flowing as a gas-liquid two-phase flow in the piping of the heat exchanger has a density difference of several tens of times between the liquid refrigerant and the gas refrigerant, and the flow rates of the gas-liquid two-phase are also greatly different. . Therefore, the refrigerant flowing in the gas-liquid two-phase state is disturbed at the gas-liquid interface, and the flow of the refrigerant becomes complicated and unstable. Therefore, the refrigerant consisting of two phases of gas and liquid is distributed to each refrigerant pipe of the heat exchanger of the indoor unit or the outdoor unit so that the refrigerant works efficiently in the heat exchanger of the indoor unit or the outdoor unit. It is necessary to distribute stably at a ratio.

  In addition, since the liquid refrigerant may be biased in the pipe due to the action of gravity on the flowing liquid refrigerant, in consideration of the influence of gravity acting on the refrigerant, the gas-liquid two-phase is applied to each refrigerant pipe of the heat exchanger. It is necessary to stably distribute the refrigerant consisting of the above at a predetermined distribution ratio.

  In addition, when the refrigerant flow rate is lower than during rated operation, such as when operating at a speed lower than the rated speed, the flow rate of the refrigerant differs from that during rated operation, and the flow configuration varies. Therefore, it is necessary to appropriately distribute the refrigerant composed of the gas-liquid two phases according to the fluctuation of the rotation speed.

  In the refrigerant distributor described in Patent Document 1 (Japanese Patent Application Laid-Open No. 2013-002688), a header pipe (header pipe) installed in the vertical direction is provided as a distribution unit, and a plurality of pipes (flat tubes) are provided on the header pipe. ) In the horizontal direction, and by providing concentric or spiral ribs as a refrigerant guiding structure inside the header pipe, the mixing of the gas refrigerant and the liquid refrigerant is promoted and the refrigerant is evenly distributed. I am doing so.

JP 2013-002688 A

  In the refrigerant distributor described in Patent Document 1, when the flow rate of the liquid refrigerant is small, the flow rate of the liquid refrigerant becomes low, so that the liquid refrigerant easily flows along the wall surface of the refrigerant induction structure. Mixing of liquid refrigerant and liquid refrigerant is not promoted, and the effect of evenly distributing the refrigerant to a plurality of downstream pipes (refrigerant pipes) is hardly obtained. Therefore, there is a problem that the performance at a low flow rate is remarkably lowered. Further, the structure inside the header pipe becomes extremely complicated, and the manufacturing cost increases.

  An object of the present invention is to use a refrigerant distributor capable of stably distributing a refrigerant to each refrigerant pipe while suppressing an increase in cost under flow conditions from a rated operating condition to a low rotation operating condition, and the same. The object is to obtain a refrigeration cycle apparatus.

  The refrigerant distributor of the present invention includes an inlet pipe, a header pipe to which the inlet pipe is connected, a plurality of refrigerant pipes that are vertically below the inlet pipe and connected to one end side of the header pipe, A distributor in which refrigerant flowing into the header pipe from the inlet pipe is distributed to the plurality of refrigerant pipes, the header pipe being connected to the header pipe at one end to which the refrigerant pipe is connected. It arrange | positions so that the vertical direction upper side of may incline.

  According to the present invention, the refrigerant distributor capable of stably distributing the refrigerant to each refrigerant pipe while suppressing an increase in cost under flow conditions from the rated operation condition to the low rotation operation condition, and the same are used. A refrigeration cycle apparatus can be provided.

1 is a refrigerant circuit diagram of a refrigeration cycle apparatus (home air conditioner) according to Embodiment 1 of the present invention. Sectional drawing of the refrigerant distributor which concerns on Example 1 of this invention. The diagram explaining the reduction effect of the liquid refrigerant distribution amount relative variation degree to a refrigerant pipe. Sectional drawing of the refrigerant distributor which concerns on Example 2 of this invention. Sectional drawing of the refrigerant distributor which concerns on Example 3 of this invention. Sectional drawing of the refrigerant distributor which concerns on Example 4 of this invention. Sectional drawing of the refrigerant distributor which concerns on Example 5 of this invention. Sectional drawing of the refrigerant distributor which concerns on Example 6 of this invention.

  Hereinafter, specific examples of the refrigerant distributor of the present invention and the refrigeration cycle apparatus including the refrigerant distributor will be described with reference to the drawings. Note that, in each drawing, the portions denoted by the same reference numerals indicate the same or corresponding portions.

  The refrigerant distributor of the present embodiment includes an inlet pipe, a header pipe to which the inlet pipe is connected, and a plurality of refrigerant pipes that are vertically below the inlet pipe and connected to one end side of the header pipe. The distributor is configured to distribute the refrigerant flowing into the header pipe from the inlet pipe to the plurality of refrigerant pipes, and the header pipe is arranged so that a vertical upper side of the header pipe is inclined to one end side to which the refrigerant pipe is connected. The According to the refrigerant distributor of the present invention, the flow rate from the rated operating condition to the low-rotation operating condition is provided by arranging the header pipe so that the upper side in the vertical direction of the header pipe is inclined at one end side to which the refrigerant pipe is connected. Even under the conditions, it is possible to stably distribute the refrigerant to each refrigerant pipe while suppressing an increase in cost and generation of energy loss.

  A first embodiment of the present invention will be described with reference to FIGS. First, a domestic air conditioner as a refrigeration cycle apparatus to which the refrigerant distributor of this embodiment is applied will be described, and then the refrigerant distributor of this embodiment will be described.

  FIG. 1 is an example of a refrigerant circuit diagram of a domestic air conditioner as a refrigeration cycle apparatus in the first embodiment. As shown in FIG. 1, a home air conditioner (hereinafter referred to as “air conditioner”) 100 according to the present embodiment has a general configuration, and includes a compressor 1, a four-way valve 2, and an electric valve. A cooling / heating throttle device 3, an indoor heat exchanger 4, and an outdoor heat exchanger 5 are connected in a ring shape with a refrigerant pipe 14.

  The air conditioner 100 switches the four-way valve 2 to perform a cooling operation using the indoor heat exchanger 4 as an evaporator and the outdoor heat exchanger 5 as a condenser, and the indoor heat exchanger 4 as a condenser and an outdoor heat exchange. The heating operation using the vessel 5 as an evaporator is performed. In FIG. 1, the solid line arrow X indicates the refrigerant circulation direction during the cooling operation, and the broken line arrow Y indicates the refrigerant circulation direction during the heating operation.

  For example, in the air conditioner 100 during cooling operation, the high-temperature and high-pressure refrigerant compressed by the compressor 1 passes through the four-way valve 2 and flows into the outdoor heat exchanger 5 and dissipates heat by heat exchange with air. Condensed. Thereafter, the refrigerant undergoes isoenthalpy expansion by the cooling / heating throttle device 3 and flows into the indoor heat exchanger 4 as a gas-liquid two-phase flow in which gas refrigerant and liquid refrigerant are mixed at low temperature and low pressure. Then, the liquid refrigerant in the indoor heat exchanger 4 is vaporized into a gaseous refrigerant by an endothermic action from the air through the refrigerant pipe 11 and fins (not shown) attached thereto. That is, when the liquid refrigerant is vaporized, the indoor heat exchanger 4 cools the surrounding air, so that the air conditioner 100 exhibits a cooling function.

  The refrigerant that has exited the indoor heat exchanger 4 returns to the compressor 1 and is compressed to high temperature and high pressure, and flows into the outdoor heat exchanger 5 through the four-way valve 2. In the outdoor heat exchanger 5, it is liquefied into a liquid refrigerant through the refrigerant pipe 12 and fins (not shown) attached thereto. Then, it circulates through the cooling / heating throttle device 3 and the indoor heat exchanger 4. Such a circulation of the refrigerant is repeated to constitute a refrigeration cycle. In addition, although the above air conditioners 100 described the general structure, in applying this invention, it is not limited to the said structure.

  FIG. 2 is a cross-sectional view illustrating the configuration of the refrigerant distributor in the first embodiment. The refrigerant distributor according to this embodiment includes the refrigerant distributor 21 of the indoor heat exchanger 4 and the outdoor heat exchanger 5 into which a gas-liquid two-phase flow in which a gas refrigerant and a liquid refrigerant are mixed flows depending on an operation mode of cooling and heating. Applies to at least one of ˜24. In the following description, the refrigerant distributor 21 will be described as a representative.

  The refrigerant distributor 21 of the present embodiment includes a header pipe 30, an inlet pipe 31 into which a refrigerant in which a gas refrigerant and a liquid refrigerant are mixed, and a plurality of refrigerant pipes 32 through which the refrigerant flows out. Fins (not shown) are connected to the refrigerant pipe 32. A plurality of refrigerant tubes 32 are connected to the header tube 30 below the inlet tube 31 in the vertical direction. The header pipe 30, the inlet pipe 31, and the refrigerant pipe 32 are made of a metal material having a high thermal conductivity such as copper. The inlet pipe 31 and the refrigerant pipe 32 are connected to the header pipe 30 by brazing or welding so as to form a refrigerant flow path therein.

  Here, as a structure for guiding the liquid refrigerant to the refrigerant pipe 32 side, the upper side of the header pipe 30 is the one end side 43 (the refrigerant pipe into which the refrigerant flows from the header pipe 30), which is the connection side of the refrigerant pipe 32 and the header pipe 30. 32 toward the inlet 32 side) and is inclined at an angle θ with respect to the vertical direction. That is, the header pipe 30 is arranged on the one end side 43 to which the refrigerant pipe 32 is connected so that the upper side in the vertical direction of the header pipe 30 is inclined.

  By arranging the header pipe 30 so as to be inclined as described above, a large amount of liquid refrigerant flowing through the header pipe 30 flows on the wall surface on the inlet side of the refrigerant pipe 32 on the inner surface of the header pipe 30. As a result, since the liquid refrigerant is also distributed to the refrigerant pipe 32 connected to the upper part of the header pipe 30, the liquid refrigerant is prevented from flowing down the inner surface of the header pipe 30 and collecting in the lower part of the header pipe 30. Thus, it is possible to improve the bias of refrigerant distribution to the plurality of refrigerant tubes 32.

FIG. 3 shows the relationship (numerical simulation result) between the inclination angle (inclination angle) θ of the header pipe 30 and the relative variation degree of the liquid refrigerant distribution amount to the plurality of refrigerant pipes 32.
As shown in FIG. 3, it was possible to confirm the effect of reducing the relative variation degree of the refrigerant distribution amount of at least 10% or more when the inclination angle θ of the header pipe is in the range of 10 ° to 90 °. Therefore, it is preferable that the header tube inclination angle θ is 10 ° or more and 90 ° or less.

  Here, considering the amount of reduction in the relative variation degree of the refrigerant distribution amount, the relative variation degree is more preferably 50% or less. Therefore, from such a viewpoint, it is more preferable that the header tube inclination angle θ is 30 ° or more and 50 ° or less.

  On the other hand, when the header tube inclination angle θ is 45 ° or more, the relative variation degree of the refrigerant distribution amount increases. Further, as the inclination angle θ of the header pipe increases, a larger installation area is required. Accordingly, the header tube inclination angle θ is preferably 45 ° or less (if the same effect can be obtained, the header tube inclination angle θ is preferably as small as possible, for example, at 30 ° and 50 ° where the relative variation is the same 50%. If so, 30 ° is more preferable.) Therefore, from such a viewpoint, the header tube inclination angle θ is more preferably 10 ° or more and 45 ° or less.

  Furthermore, in consideration of the effect of reducing the relative variation degree of the refrigerant distribution amount (variation degree 50% or less) and the installation area, the inclination angle θ of the header pipe is most preferably 30 ° or more and 45 ° or less.

  Next, Embodiment 2 of the refrigerant distributor of the present invention will be described with reference to FIG. In the present embodiment, the header pipe 30 has a protrusion 34 that protrudes from the inner wall surface of the header pipe 30 between the inlet pipe 31 and the refrigerant pipe 32, and the protrusion 34 is formed by the refrigerant pipe 32. There is an inclined portion that is inclined downward in the vertical direction toward one end side 43 of the connected header pipe 30. In the present embodiment, the protrusion 34 is formed on the entire circumference of the inner wall surface of the header tube 30.

  FIG. 4 is a cross-sectional view of the refrigerant distributor 21 in the second embodiment. 4A is an enlarged cross-sectional view showing an upper portion of the header pipe 30 and a portion of the inlet pipe 31 and the refrigerant pipe 32 connected to the header pipe 30, and FIG. 4B is an inside view of the header pipe 30. It is the shape figure which looked at from the header pipe 30 longitudinal direction.

  In the present embodiment, the protrusion 34 described above is installed on the inner wall surface of the header pipe 30 between the downstream side of the refrigerant flow in the inlet pipe 31 and the upstream side of the refrigerant pipe 32. The protruding portion 34 is installed so as to protrude from the inner wall surface of the header pipe 30 and is configured to be inclined downward toward the direction of the connecting portion between the refrigerant pipe 32 and the header pipe 30. The protrusion 34 is formed in the entire circumferential direction of the inner wall of the header tube 30, and it is desirable that the protruding portion has a protruding amount of a thickness that allows liquid refrigerant to flow from the inner wall surface of the header tube 30 in a liquid film shape. Note that the number of protrusions 34 may be one, or a plurality of protrusions 34 as shown in FIG.

  Due to the protrusions 34, the liquid refrigerant flowing through the header pipe 30 flows more on the inner surface of the header pipe 30 to the wall surface on the inlet side of the refrigerant pipe 32. As a result, since the liquid refrigerant is also distributed to the refrigerant pipe 32 connected to the upper part of the header pipe 30, the liquid refrigerant is prevented from flowing down the inner surface of the header pipe 30 and collecting in the lower part of the header pipe 30. Thus, it is possible to improve the bias of refrigerant distribution to the plurality of refrigerant tubes 32.

  As the method for forming the protrusion 34, the protrusion 34 is formed by fixing the protrusion 34 by cutting, brazing or welding on the inner surface of a long plate-shaped metal plate, and the end surfaces of the metal plates are By fixing by brazing or welding, it can be formed into a pipe shape having the protrusions 34. Alternatively, the upper part of the header pipe 30 including the protruding part 34 is formed as a separate metal part including the insertion part of the inlet pipe 31 and the header pipe 30, and the protruding part 34 is formed therein, and then the inlet pipe 31 and the header pipe are formed. 30 may be inserted and fixed by brazing or welding. At this time, the component can be formed by dividing the component into a plurality of components, fixing the protruding portion 34 by cutting, brazing, or welding, and then fixing the divided components by brazing or welding.

  More simply, the protrusion 34 is formed by punching or the like from a metal thin plate made of the same material as the header tube 30 such as copper, and the metal thin plate is rolled up. Thereafter, a roll-shaped thin metal plate provided with an opening so as not to obstruct the refrigerant flow from the inlet pipe 31 is inserted from the top of the header pipe 30, and the thin metal sheet is fixed by brazing or welding, and the header pipe 30 is The protrusion 34 can be formed by sealing the upper end.

  Further, in addition to the protruding portion 34 in the present embodiment, the header pipe 30 is inclined and installed as described in the first embodiment, so that the protruding portion 34 can connect the refrigerant pipe 32 and the header pipe 30 to each other. Since the liquid refrigerant can be biased toward the direction side and the liquid refrigerant can be further biased toward the direction side of the connecting portion between the refrigerant pipe 32 and the header pipe 30 by tilting the header pipe 30, the inclination angle θ of the header pipe (see FIG. Even when (see 2) is small, the distribution bias of the liquid refrigerant can be reduced. Therefore, since the header pipe inclination angle θ can be reduced, the refrigerant distributor including the header pipe 30 can be installed in a smaller space.

  Next, Embodiment 3 of the refrigerant distributor of the present invention will be described with reference to FIG. In the present embodiment, in particular, the protrusion 34 has a notch 40 in the longitudinal direction of the header pipe 30 in the connecting portion between the refrigerant pipe 32 and the header pipe 30.

  FIG. 5 is a cross-sectional view of the refrigerant distributor 21 in the third embodiment. FIG. 5A is an enlarged cross-sectional view showing an upper portion of the header pipe 30 and a portion of the inlet pipe 31 and the refrigerant pipe 32 connected to the header pipe 30, and FIG. It is the shape figure which looked at from the header pipe 30 longitudinal direction. In the third embodiment, as shown in FIG. 5 (B), a protrusion 34 having a different configuration is provided with respect to the protrusion 34 in the second embodiment.

  As shown in FIG. 5B, in this embodiment, the protruding portion 34 is not formed in the entire circumferential direction of the inner wall of the header pipe, and a notch 40 is formed above the inlet portion of the refrigerant pipe 32. Is. The width of the notch 40 can be set to an arbitrary value, but is desirably larger than the inner diameter of the refrigerant pipe 32. The protruding portion 34 is formed with a downward slope on the direction side of the connecting portion between the refrigerant pipe 32 and the header pipe 30, and the notch 40 is formed above the inlet portion of the refrigerant pipe 32. Therefore, liquid refrigerant flows in a concentrated manner on the direction side of the connection portion between the refrigerant pipe 32 and the header pipe 30. According to this embodiment, even when the flow rate of the inner wall surface of the header pipe 32 of the liquid refrigerant is high, it is possible to suppress the upstream flow of the refrigerant pipe 32 from being separated from the wall surface of the header pipe 30.

  Next, Embodiment 4 of the refrigerant distributor of the present invention will be described with reference to FIG. In this embodiment, in particular, the protrusion 34 is formed such that the protrusion width 41 of the protrusion 34 on the one end side 43 to which the refrigerant pipe 32 is connected is smaller than the protrusion width 42 on the opposite side to the one end side 43. is there.

  FIG. 6 is a cross-sectional view of the refrigerant distributor 21 in the fourth embodiment. 6A is an enlarged cross-sectional view showing an upper portion of the header pipe 30 and a portion of the inlet pipe 31 and the refrigerant pipe 32 connected to the header pipe 30, and FIG. 6B is an inside view of the header pipe 30. It is the shape figure which looked at from the header pipe 30 longitudinal direction. In the fourth embodiment, with respect to the protrusions 34 in the second and third embodiments, as shown in FIG. 6B, a protrusion 34 having a different configuration is provided.

  That is, the protrusion 34 in the fourth embodiment does not form the protrusion 34 on the inner wall of the header pipe 30 with a uniform protrusion amount (protrusion width) in the circumferential direction, but in the inlet direction of the refrigerant pipe 32. The amount of protrusion is non-uniform in the circumferential direction, such as by reducing the amount of protrusion. Also in this embodiment, since the protruding portion 34 is formed with a downward slope on the direction side of the connecting portion between the refrigerant pipe 32 and the header pipe 30, the connection between the refrigerant pipe 32 and the header pipe 30 is provided. The liquid refrigerant is concentrated and flows on the direction side of the portion, and the flow of the liquid refrigerant flowing down the wall surface of the header pipe 30 and the protrusion 34 collide with each other. Even when the temperature is fast, it is possible to prevent the liquid refrigerant flow on the upstream side of the refrigerant pipe 32 from being separated from the wall surface of the header pipe 30.

  Next, Embodiment 5 of the refrigerant distributor of the present invention will be described with reference to FIG. FIG. 7 is a cross-sectional view of the refrigerant distributor 21 in the fifth embodiment. Similarly to the first embodiment described with reference to FIGS. 1 to 3, the refrigerant distributor 21 according to the present embodiment is also a gas-liquid two-phase flow in which a gas refrigerant and a liquid refrigerant are mixed according to the operation mode of cooling and heating. Is applied to at least one of the refrigerant distributors 21 to 24 of the indoor heat exchanger 4 and the outdoor heat exchanger 5 into which the refrigerant flows. In the following description, the case where the fifth embodiment is applied to the refrigerant distributor 21 shown in FIG. 1 will be described as a representative.

  The refrigerant distributor 21 in the fifth embodiment also has basically the same configuration as the refrigerant distributor of the first embodiment described with reference to FIG. That is, the refrigerant distributor 21 of the fifth embodiment shown in FIG. 7 also includes a header pipe 30, an inlet pipe 31 into which a refrigerant in which a gaseous refrigerant and a liquid refrigerant are mixed, and a plurality of refrigerant pipes 32 from which the refrigerant flows out. Yes. The plurality of refrigerant tubes 32 are connected to the header tube 30 below the inlet tube 31 in the vertical direction. The inlet pipe 31 and the refrigerant pipe 32 are connected to the header pipe 30 by brazing or welding, and form a refrigerant flow path therein. The inlet pipe 31 is installed above a connection portion between the plurality of refrigerant pipes 32 and the header pipe 30.

The difference between the fifth embodiment and the first to fourth embodiments will be described below.
In this embodiment, the header pipe 30 is composed of a header pipe (upper header pipe) 30a on the upper side in the vertical direction and a header pipe (lower header pipe) 30b on the lower side in the vertical direction. The upper header pipe 30a is a header pipe arranged above the refrigerant pipe 32 at the top in the vertical direction, and the lower header pipe 30b is arranged below the upper header pipe 30a. It is a header tube.

As a structure for guiding the liquid refrigerant to the refrigerant pipe 32 side, in this embodiment, the refrigerant flows in from the one end side 43 that is the connection side of the refrigerant pipe 32 and the header pipe 30, that is, the header pipe 30. toward the inlet side of the tube 32, the upper side header pipe 30a is, relative to the vertical direction, are disposed inclined at any angle theta ₁ angle. The lower side header pipe 30b is based on the vertical direction, are disposed at 0 ° greater than the angle theta ₁ is less than the angle theta _2.

  The upper header pipe 30a and the lower header pipe 30b may be joined by brazing, welding, or the like, or one header pipe 30 may be formed above the uppermost refrigerant pipe 32. You may make it bend | fold at a part and form the part of the upper side header pipe | tube 30a and the part of the lower side header pipe | tube 30b. About another structure, it is the same as that of the refrigerant | coolant distribution piping of Example 1 demonstrated in FIG.

  By configuring the refrigerant distribution pipe 21 as in the fifth embodiment, more liquid refrigerant flows through the header pipe 30 on the wall surface on the inlet side of the refrigerant pipe 32 on the inner face of the header pipe 30. It begins to flow. As a result, since the liquid refrigerant is also distributed to the refrigerant pipe 32 connected to the upper part of the header pipe 30, the liquid refrigerant is prevented from flowing down the inner surface of the header pipe 30 and collecting in the lower part of the header pipe 30. Thus, it is possible to improve the bias of refrigerant distribution to the plurality of refrigerant tubes 32.

Furthermore, installation in the present embodiment, since the the lower side header pipe 30b to be placed at 0 ° greater than the angle theta ₁ is less than the angle theta _2, than when installing the entire header pipe 30 at an angle theta ₁ The area can be reduced. Therefore, according to the present Example, the whole heat exchanger can be reduced in size and the freedom degree of installation of a heat exchanger or a refrigerant distributor can be improved.

Incidentally, in the fifth embodiment described above, ₁ the inclination angle of the upper side header pipe 30a _theta, but the angle of inclination of the lower side header pipe 30b is made larger and the angle theta ₁ is less than the angle theta ₂ than 0 °, the lower The side header pipe 30b may be configured with an inclination angle of 0 °, that is, in the vertical direction.

With reference also results obtained by numerical simulation of Figure 3 described in the first embodiment, the inclination angle theta ₁ of the upper side header pipe 30a, as well as the inclination angle theta of the header tubes described in Example 1 If well, most preferably it may be at 45 ° below the inclination angle theta ₁ 30 ° or more. Also, the lower side header pipe 30b inclination angle theta ₂ of, 0 is preferable to the ° or 20 ° or less, further preferably to greater than 20 ° than 0 °. Thereby, the relative variation degree of the liquid refrigerant distribution amount to the plurality of refrigerant pipes 32 can be reduced, and the installation area of the header pipe 30 can be reduced.

In the present embodiment, it may be connected as different angles of inclination angle theta ₂ of the upper side of the header pipe 30a inclination angle theta ₁ and the lower side header pipe 30b, the inclination angle of the lower side header pipe 30b theta ₂ Is also included that is larger than the inclination angle θ ₁ of the upper header tube 30a.

  Next, Embodiment 6 of the refrigerant distributor of the present invention will be described with reference to FIG. FIG. 8 is a sectional view of the refrigerant distributor 21 in the sixth embodiment. The refrigerant distributor 21 according to the present embodiment also has the refrigerant of the indoor heat exchanger 4 and the outdoor heat exchanger 5 into which the gas-liquid two-phase flow flows, similarly to the first embodiment described with reference to FIGS. An example applied to at least one of the distributors 21 to 24 and applied to the refrigerant distributor 21 shown in FIG.

Since the refrigerant distributor 21 in the present embodiment also has basically the same configuration as the refrigerant distributor of the first embodiment described with reference to FIG. 2, the description of the same parts is omitted.
The difference between the sixth embodiment and the first to fifth embodiments will be described below.

In the present embodiment, the entire header pipe 30 has a curved pipe shape as a structure for guiding the liquid refrigerant to the refrigerant pipe 32 side. More specifically, the vertical direction of the header pipe 30 is directed toward the one end side 43 that is the connection side of the refrigerant pipe 32 and the header pipe 30, that is, toward the inlet portion side of the refrigerant pipe 32 through which the refrigerant flows from the header pipe 30. The upper end side is inclined at an arbitrary angle θ ₁ with respect to the vertical direction, and the vertical lower end side of the header pipe 30 is greater than 0 ° with respect to the vertical direction. It is installed at an angle θ ₂ smaller than ₁ . In addition, a portion between the vertical upper end side and the vertical lower end side of the header pipe 30 is continuously connected with an arbitrary curvature.

  Therefore, the header tube 30 in the present embodiment is formed in a curved shape such as a convex shape or a curved shape such as an arc shape. Further, the curve shape constituting the header pipe 30 may be constituted by a spline curve or a Bezier curve, but is not limited to these curve types, and may be constituted by other different curve types. good.

  According to the sixth embodiment, as in the first embodiment, the liquid refrigerant flowing through the header pipe 30 flows more on the wall surface on the inlet side of the refrigerant pipe 32 on the inner face of the header pipe 30. Become. As a result, the liquid refrigerant is also distributed to the refrigerant pipe 32 connected to the upper part of the header pipe 30, so that the liquid refrigerant flows down the inner surface of the header pipe 30 and flows into the lower part of the header pipe 30. Accumulation of the refrigerant is suppressed, and uneven distribution of the refrigerant to the plurality of refrigerant pipes 32 can be improved.

Further, according to the sixth embodiment, the vertical upper end side of the header pipe 30 is installed at an angle of θ ₁ with respect to the vertical direction, and the vertical lower end side of the header pipe 30 is installed. Is installed at an angle θ ₂ that is larger than 0 ° and smaller than the angle θ _{1 with} respect to the vertical direction, so that, as in the fifth embodiment, the entire header pipe 30 is installed at an angle θ _1. Can also reduce the installation area. Therefore, also according to the present embodiment, the entire heat exchanger can be further reduced in size, and the degree of freedom of installation of the heat exchanger and the refrigerant distributor can be improved.

Also, by way of example 5 described above, since the connecting portion of the upper side header pipe 30a and the lower header pipe 30b are connected at different angles, the inclination angle theta ₁ of the upper side header pipe 30a and the lower header pipe 30b when it becomes angular difference inclination angle theta ₂ is large, the liquid refrigerant flowing down the inlet side of a wall surface of the refrigerant pipe 32 in the header pipe 30 inner surface, at the connection portion of the upper side header pipe 30a and the lower header pipe 30b Flow separation may occur. For this reason, the amount of liquid refrigerant flowing down the wall surface of the header pipe 30 on the inlet side of the refrigerant pipe 32 may be reduced. On the other hand, according to the sixth embodiment, since the header pipe 30 is continuously connected in a curved shape, it is possible to suppress the flow of the liquid refrigerant from being separated from the wall surface of the inner surface of the header pipe 30. There is an effect that can be done.

In the sixth embodiment described above, the vertical upper end side of the header pipe 30 is inclined at an angle θ ₁ with respect to the vertical direction, and the vertical lower end side of the header pipe 30 is 0 °. Although the angle θ ₂ is larger and smaller than the angle θ ₁ , the inclination angle may be 0 °, that is, the vertical direction on the lower end portion in the vertical direction.

Further, in the same manner as in Example 5, wherein the vertical upper end inclination angle theta ₁ of may be the same as the inclination angle theta of the header tubes described in the first embodiment. That is, the inclination angle theta ₁ preferably be in the range less than 45 ° or more 10 °, more preferably may be at 45 ° or less 30 ° or more. Also, the for vertically lower end of the tilt angle theta _2, preferably to 0 ° or 20 ° or less, further preferably below 0 ° 20 ° greater than. Thereby, the relative variation degree of the liquid refrigerant distribution amount to the plurality of refrigerant pipes 32 can be reduced, and the installation area of the header pipe 30 can be reduced.

In the description of the sixth embodiment, the vertical upper end portion of the header pipe 30 is inclined at an angle θ ₁ with respect to the vertical direction, and the vertical lower end portion is larger than 0 ° and the angle θ _The example in which the angle θ ₂ is smaller than ₁ has been described. That is, the example in which the curved shape is formed so as to protrude upward has been described, but the curved shape may be formed so as to protrude downward. That is, the vertical upper end portion side of the header pipe 30 is inclined at an angle θ ₁ with respect to the vertical direction, and the vertical lower end side is set to an angle θ ₂ larger than the angle θ ₁ . About the part between the vertical direction upper end part side and the vertical direction lower end part side, you may make it connect continuously by arbitrary curvatures.

  In addition, this invention is not limited to the Example mentioned above, Various modifications are included. The above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.

1: compressor, 2: four-way valve, 3: air conditioner throttle device,
4: Indoor heat exchanger, 5: Outdoor heat exchanger,
11, 12, 32: refrigerant pipe,
14: Refrigerant piping,
21-24: Refrigerant distributor,
30: header pipe, 30a: vertical upper header pipe, 30b: vertical lower header pipe,
31: Inlet pipe, 34: Projection
40: Notch part, 41.42: Projection width, 43: One end side,
100: Home air conditioner (refrigeration cycle apparatus).

Claims (18)

An inlet pipe, a header pipe connected to the inlet pipe, and a plurality of refrigerant pipes vertically below the inlet pipe and connected to one end side of the header pipe, from the inlet pipe A refrigerant distributor in which the refrigerant flowing into the header pipe is distributed to the plurality of refrigerant pipes,
The refrigerant distributor according to claim 1, wherein the header pipe is disposed on the one end side to which the refrigerant pipe is connected so that an upper side in the vertical direction of the header pipe is inclined.   2. The refrigerant distributor according to claim 1, wherein an angle formed by the header pipe and a vertical direction is not less than 10 ° and not more than 90 °.   2. The refrigerant distributor according to claim 1, wherein an angle formed between the header pipe and the vertical direction is not less than 30 ° and not more than 50 °.   2. The refrigerant distributor according to claim 1, wherein an angle formed between the header pipe and the vertical direction is 10 ° to 45 °. 3.   2. The refrigerant distributor according to claim 1, wherein an angle formed between the header pipe and the vertical direction is not less than 30 ° and not more than 45 °. The refrigerant distributor according to any one of claims 1 to 5,
The header pipe is between the inlet pipe and the refrigerant pipe, and has a protruding portion protruding from the inner wall surface of the header pipe,
The refrigerant distributor according to claim 1, wherein the protrusion has an inclined portion that is inclined downward in the vertical direction toward the one end side to which the refrigerant pipe is connected.   The refrigerant distributor according to claim 6, wherein the protrusion is formed on the entire circumference of the inner wall surface of the header pipe.   7. The refrigerant distributor according to claim 6, wherein the projecting portion has a notch portion above a connection portion between the refrigerant tube and the header tube in a longitudinal direction of the header tube.   The refrigerant distributor according to claim 6, wherein a protruding width of the protruding portion on the one end side to which the refrigerant pipe is connected is smaller than a protruding width on the opposite side to the one end side. . An inlet pipe, a header pipe connected to the inlet pipe, and a plurality of refrigerant pipes vertically below the inlet pipe and connected to one end side of the header pipe, from the inlet pipe A refrigerant distributor in which the refrigerant flowing into the header pipe is distributed to the plurality of refrigerant pipes,
The header tube is
The one end side to which the refrigerant pipe is connected is arranged so that the vertical upper side of the header pipe is inclined,
An upper header pipe disposed above the refrigerant pipe, and a lower header pipe disposed below the upper header pipe,
The refrigerant distributor, wherein the inclination angle of the upper header pipe and the inclination angle of the lower header pipe are connected as different angles. The refrigerant distributor according to claim 10, wherein
The upper header pipe is inclined at an arbitrary angle θ ₁ with respect to the vertical direction toward the one end side to which the refrigerant pipe is connected, and the lower header pipe has a vertical direction. The refrigerant distributor is installed at an angle θ ₂ smaller than the angle θ _{1 as a} reference. 12. The refrigerant distributor according to claim 11, wherein the inclination angle θ ₁ of the upper header pipe is 10 ° to 45 ° with respect to the vertical direction, and the inclination angle θ ₂ of the lower header pipe is vertical. A refrigerant distributor, characterized in that an angle with the direction is 0 ° or more and 20 ° or less. 13. The refrigerant distributor according to claim 12, wherein an inclination angle θ ₁ of the upper header pipe is 30 ° to 45 ° with respect to a vertical direction, and an inclination angle θ ₂ of the lower header pipe is vertical. A refrigerant distributor characterized in that an angle formed with a direction is greater than 0 ° and 20 ° or less. An inlet pipe, a header pipe connected to the inlet pipe, and a plurality of refrigerant pipes vertically below the inlet pipe and connected to one end side of the header pipe, from the inlet pipe A refrigerant distributor in which the refrigerant flowing into the header pipe is distributed to the plurality of refrigerant pipes,
The header tube is
The refrigerant distributor, wherein the one end side to which the refrigerant pipe is connected is disposed so that a vertical upper side of the header pipe is inclined, and the entire header pipe is formed in a curved pipe shape. . In the refrigerant distributor according to claim 14, a header pipe of the curved pipe shape, with its vertical direction upper portion side, relative to the vertical direction, is disposed inclined at any angle theta ₁ angle, said header The vertical lower end side of the pipe is installed at an angle θ ₂ smaller than the angle θ _{1 with} respect to the vertical direction, and a portion between the vertical upper end side and the vertical lower end side of the header pipe is The refrigerant distributor is connected continuously with an arbitrary curvature. 16. The refrigerant distributor according to claim 15, wherein an inclination angle θ ₁ on the upper end side in the vertical direction of the header pipe is 10 ° or more and 45 ° or less with respect to the vertical direction, and a lower end portion in the vertical direction of the header pipe. The refrigerant distributor is characterized in that the side inclination angle θ ₂ is 0 ° or more and 20 ° or less with respect to the vertical direction. 17. The refrigerant distributor according to claim 16, wherein an inclination angle θ ₁ on the upper end side in the vertical direction of the header pipe is 30 ° or more and 45 ° or less with respect to the vertical direction, and a lower end portion in the vertical direction of the header pipe. refrigerant distributor, characterized in that the inclination angle theta ₂ side is the angle between the vertical direction is 20 ° or less larger than 0 °.   A refrigeration cycle apparatus comprising the refrigerant distributor according to any one of claims 1 to 17.

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