JP3387387B2 - Refrigerant distributor and refrigeration cycle device using the same - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant distributor used in a refrigeration cycle device such as an air conditioner or a refrigeration device.

[0002]

2. Description of the Related Art In a heat exchanger that functions as a condenser or an evaporator of a refrigeration cycle apparatus such as an air conditioner or a refrigeration apparatus, when an internal refrigerant flow path is divided into a plurality of paths,
A refrigerant distributor for distributing the refrigerant to each path is required at the inlet of the heat exchanger. In addition, for example, in a multi-type air conditioner in which a plurality of outdoor units and indoor units are connected in parallel, a refrigerant distributor is required to distribute the refrigerant from the main refrigerant passage to each unit. Generally, the refrigerant that has passed through the expansion valve of the refrigeration cycle device and the refrigerant at the inlet of the evaporator are in a gas-liquid two-phase state of a gas refrigerant and a liquid refrigerant, and a density distribution occurs in the cross section of the refrigerant flowing in the pipe. . For example, if there is a bend in the inflow pipe, due to the effect of centrifugal force, and if the inflow pipe and the refrigerant distributor main body are horizontally arranged, due to the effect of gravity, the liquid refrigerant is biased to flow unevenly on the inner surface of one pipe. The phenomenon occurs. Therefore, in the refrigerant distributor, the phenomenon of non-uniform flow as described above does not occur, the separation of gas and liquid can be prevented, the refrigerant is homogeneously mixed, and the gas-liquid mass flow ratio at the refrigerant distributor inlet and the refrigerant distributor. A function of distributing the refrigerant in a state where the gas-liquid mass flow rate ratio at the outlet is uniform is required.

As a conventional refrigerant distributor, Japanese Patent Laid-Open No. 2-16
6366 publication is mentioned. FIG. 15 is a sectional view showing this refrigerant distributor. In the figure, 13 is a refrigerant distributor main body, 15 is a throttle part, 16 is an inflow pipe, 17 is a collision wall, 18
Is the peripheral wall, 19 is the inlet of the outflow pipe 21, and 20 is the outflow pipe 21.
And 21 is an outflow pipe. The conventional refrigerant distributor is
The inflow pipe 16 and the plurality of outflow pipes 21 are connected to the refrigerant distributor main body 13, respectively, and a branch space composed of the collision wall 17 and the peripheral wall 18 is formed inside the refrigerant distributor main body 13 to move from the inflow pipe 16 to the branch space. A narrowed portion 15 is provided in the flow path that reaches. When the inlet pipe diameter is D1, the peripheral wall inner diameter is D2, the throttle diameter is L1, and the distance from the throttle portion 15 to the collision wall 17 is L2, D2 / D1 <2.0, L1 / D1 <0.5,
L2 <30 mm.

In the refrigerant distributor configured as described above, the refrigerant flowing from the inflow pipe 16 is jetted into the branch space by the throttle portion 15 and collided with the collision wall 17 of the branch space to make the gas-liquid two-phase flow uniform. Promote. Then, the branch space is distributed to the plurality of outflow pipes 21. By making the branch space small to some extent, formation of a liquid pool or an air pool is eliminated, and the distribution space is evenly distributed to the outflow pipes 21. .

[0005]

Since the conventional refrigerant distributor is constructed as described above, there is a bend in the pipe upstream of the inflow pipe 16, or the inflow pipe 16 and the refrigerant distributor main body 13 are horizontal. In the case where the gas-liquid two-phase refrigerant has a non-uniform flow due to such a situation as being arranged in the above-mentioned case, by simply setting the throttle diameter L1 to L1 / D1 <0.5 with respect to the inflow pipe diameter D1, the plurality of outflow pipes 21 can be made uniform. Cannot be distributed. This is because under the above conditions alone, the gas-liquid two-phase refrigerant is used in a wide range of flow conditions, such as when the refrigerant flow velocity is slow or when the gas-liquid two-phase flow rate of the refrigerant changes and the mass flow rate of the liquid refrigerant is extremely large. This is because it is impossible to uniformly stir and mix. Further, the collision wall 17 and the peripheral wall 18
The volume of the branch space of the ^{π × (D2) 2/4} × L2
(Π: pi), D2 / D1 <2.
If only 0, L2 <30 mm, the branch space volume cannot be said to be sufficiently small when the flow velocity of the refrigerant is slow, and the gas-liquid two-phase refrigerant is separated again after passing through the throttle section 15, and the outflow pipe 21 There was a problem that it could not be distributed evenly.

The refrigerant distributor according to the present invention has been made in order to solve the above problems, and when the pipe upstream of the refrigerant distributor has a bend or the pipe or the refrigerant distributor main body is horizontal. In any installation condition of the refrigerant distributor, such as the case where the refrigerant is installed, the refrigerant is agitated and mixed without being affected by the non-uniform flow and the separation of gas and liquid does not occur. The purpose is to distribute the refrigerant.

Further, by using the refrigerant distributor according to the present invention in a refrigerating cycle device such as an air conditioner or a refrigerating device, its performance and efficiency are improved, and reliability problems due to the non-uniformity of refrigerant distribution are caused. For example, the purpose is to prevent the generation of refrigerant noise and the splashing of dew on the evaporator.

[0008]

According to a first aspect of the present invention, there is provided a refrigerant distributor, which is connected to a mixing section through which a refrigerant flowing from an inflow pipe passes, and a plurality of outflow tubes, and discharges the refrigerant flowing from the mixing section. With a branch space that distributes to each of the tubes,
Inner diameter in mixing section is D [m], length of refrigerant in flow direction
Is L [m], and the mass flow rate of the refrigerant flowing through this mixing section is W
[Kg / s], D and L satisfy L / D> 5
With, D, W is ^{W / (π × D 2/} 4)> 500
The mixing part is configured to satisfy (π: pi)
is there.

[0009]

[0010]

[0011]

A refrigerant distributor according to a second aspect of the present invention is the refrigerant distributor according to the first aspect, wherein the height of the branch space in the flow direction of the refrigerant is H [m] and the refrigerant flowing through the mixing portion is When the mass flow rate is W [kg / s], the branch space is configured to satisfy W / H> 2.

The refrigerant distributor according to claim 3 of the present invention is the refrigerant distributor according to claim 1 or 2 , wherein the volume of the branch space is V [m ³ ] and the mass of the refrigerant flowing through the mixing portion. When the flow rate is W [kg / s], the branch space is configured to satisfy W / V> 10.

[0014]

According to a fourth aspect of the present invention, there is provided a refrigeration cycle apparatus in which the refrigerant distributor according to any one of the first to third aspects is provided in a refrigerant branch portion of a refrigerant passage for circulating a refrigerant. Is.

[0016]

DETAILED DESCRIPTION OF THE INVENTION

Embodiment 1. Hereinafter, Embodiment 1 of the present invention will be described with reference to the drawings. FIG. 1 is a sectional view showing a refrigerant distributor according to the first embodiment. In FIG. 1, 1 is a refrigerant distributor body, 2 is an inflow pipe, 3a and 3b are, for example, two outflow pipes, 4
Is a mixing section composed of a thin tube, and 5 is a branch space. Also,
The arrow in the figure indicates the flow direction of the refrigerant, L is the length [m] of the mixing part 4 in the flow direction, D is the inner diameter [m] of the mixing part 4, and H is the height of the branch space 5 in the flow direction [m]. m], V is the volume [m ³ ] of the branch space 5, and W is the mass flow rate [kg / s] of the refrigerant flowing through the mixing section 4.

The refrigerant distributor body 1 has an inflow pipe 2 on one end side,
A plurality of, for example, two outflow pipes 3a and 3b are respectively connected to the other end side, and a mixing section 4 connected to the inflow pipe 2 is provided on the inflow pipe 2 side of the refrigerant distributor body 1. The mixing section 4 is composed of a thin tube and has a function of making the flow state of the inflowing gas-liquid two-phase refrigerant a homogeneous flow such as a bubbly flow or an annular spray flow. In the present embodiment, for example, the inner diameter of the mixing portion 4 is smaller than the inner diameter of the inflow pipe 2 and is significantly smaller than the length of the mixing portion 4 in the flow direction. A branch space 5 is provided between the mixing section 4 and the two outflow pipes 3a and 3b, and the refrigerant flowing from the inflow tube 2 is contracted and accelerated in the mixing section 4 and flows out through the branch space 5. The tubes 3a, 3b are distributed.

Next, the operation of distribution will be described. FIG. 2 is an explanatory diagram showing the state of the refrigerant in the horizontally arranged refrigerant distributor body 1, in which a gas-liquid two-phase refrigerant of a gas refrigerant and a liquid refrigerant flows in from an inflow pipe 2 and gas-liquid flows from an outflow pipe 3a, 3b. It shows how the two-phase refrigerant flows out. 3 is a perspective view showing an example in which the outflow pipes 3a and 3b are installed in the horizontal direction, and FIG. 4 shows the outflow pipes 3a and 3b rotated about the axis from the one shown in FIG. FIG. 3 is a perspective view showing an example of installation in the vertical direction.
As shown in FIG. 2, in the inside of the inflow pipe 2, the liquid refrigerant is unevenly distributed on the lower surface of the pipe due to the influence of gravity, and a nonuniform flow phenomenon occurs. In the present embodiment, the inner diameter D of the mixing section 4 formed of a thin tube is used.
[M], length L [m], refrigerant mass flow rate W [kg / s]
The relationship is defined as satisfying Equations 1 and 2.

L / D> 5. ． ． (1) W / (π × D 2/4)> 500. ． ． (2) π: Pi

When the mixing section 4 is constructed as described above, even if the gas-liquid two-phase refrigerant has a non-uniform flow, for example, when the pipe upstream of the inflow pipe 2 has a bend, it flows in from the inflow pipe 2. The gas-liquid two-phase refrigerant is contracted and accelerated in the mixing section 4, so that the gas-liquid two-phase refrigerant is sufficiently stirred and mixed to form a homogeneous flow.

Further, in the present embodiment, the relationship between the height H [m] and the volume V [m ³ ] of the branch space 5 satisfies the expressions 3 and 4.

[0022]     W / H> 2. ． ． (3)     W / V> 10. ． ． (4)

In particular, when the outflow pipes 3a and 3b are installed vertically as shown in FIG. 4, the liquid refrigerant is likely to be unevenly distributed in the lower outflow pipe 3a due to the influence of gravity. When the height H [m] and the volume V [m ³ ] of the branch space 5 are determined in the above, the gas-liquid two-phase refrigerant is sufficiently agitated and mixed in the branch space 5 to form a homogeneous flow, and from the outflow pipes 3a and 3b, The refrigerant in a homogeneous state flows out. For example, even if the cross-sectional area of the branch space 5 is larger than that of the mixing section 4, the volume V and the height H are calculated by the formula 3,
If it is made small so as to satisfy the relationship of Expression 4, the gas-liquid two-phase refrigerant can be homogeneously distributed to the outflow pipes 3a and 3b without forming a liquid pool or a gas pool. Here, the homogeneous state means the gas-liquid mass flow ratio flowing through the inlet of the refrigerant distributor, that is, the inflow pipe 2, and the plurality of outlets of the refrigerant distributor, that is, the outflow pipe 3.
It means that the gas-liquid mass flow rate ratios flowing through a and 3b are equal to each other.

Next, the inner diameter D [m], the length L [m] of the mixing section 4 of the refrigerant distributor according to the present embodiment, the mass flow rate W [kg / s] of the refrigerant flowing through the mixing section 4, and the branch space. Height H of 5
[M] and volume V [m ³ ] are changed, and the refrigerant distributor main body 1
The test results of the distribution ratio to the outflow pipes 3a and 3b when the installation state of is changed are shown in the graphs of FIGS. 5, 6, 7, and 8. This test is an example in which a refrigerant distributor having two outflow pipes 3a and 3b is horizontally installed and the outflow pipes 3a and 3b are vertically arranged as shown in FIG. The case where the drift of the liquid two-phase refrigerant is the largest is shown. Then, the distribution ratio [%] on the vertical axis of each drawing indicates the refrigerant distribution ratio of the lower outflow pipe 3a of the two outflow pipes 3a and 3b. Further, in each drawing, the allowable range of the distribution ratio [%] of the practical outflow pipe 3a that does not cause the performance deterioration is set to 48% to 52%, and each is shown within the range of the shaded area.

The horizontal axis of FIG. 5 is the parameter L / D (mixing unit 4
(Length / inner diameter), and the vertical axis indicates mass flow rate W = 0.01
The distribution ratio [%] when [kg / s] is shown.
As shown in the figure, the allowable range is L / D> 5, and the length L is sufficiently long with respect to the inner diameter D of the mixing section 4 in this range, so that the gas-liquid two-phase refrigerant is more effective. Homogenized. The horizontal axis parameter ^{W / (π × D 2/} 4) in FIG. 6
(Mass flow rate per unit area in cross section of mixing section 4)
The vertical axis represents the distribution ratio [%] when the length L of the mixing section 4 is 0.05 [m] and the inner diameter D is 0.005 [m]. As shown in ^{FIG., W / (π × D 2} /4)
In the range of> 500, the allowable range is established. In this range, the mass flow rate of the mixing section 4 is sufficiently high, so that the gas-liquid two-phase refrigerant is more homogenized. The horizontal axis of FIG. 7 is the parameter W / H (mass flow rate / height of the branch space 5), and the vertical axis is the mass flow rate W.
= 0.01 [kg / s], length L of the mixing part 4 = 0.05
The distribution ratio [%] when [m] and the inner diameter D = 0.005 [m] is shown. As shown in the figure, W / H> 2
In this range, the height of the branch space 5 is made sufficiently small, so that the gas-liquid two-phase refrigerant is more homogenized. The horizontal axis of FIG. 8 indicates the parameter W / V (mass flow rate /
The volume of the branch space 5), and the vertical axis indicates the mass flow rate W = 0.0.
1 [kg / s], length L of the mixing part 4 = 0.05 [m],
The distribution ratio [%] is shown when the inner diameter D is 0.005 [m]. As shown in the figure, the allowable range is in the range of W / V> 10, and since the volume of the branch space 5 is sufficiently small in this range, the gas-liquid two-phase refrigerant is more homogenized.

As described above, when the mixing section 4 constituting the refrigerant distributor is formed of a thin tube, the gas-liquid two-phase refrigerant, which was in a non-uniform flow state in the inflow tube 2, is contracted and accelerated to form a homogeneous flow. You can In particular, if the shape of the mixing portion 4 is configured to satisfy the formulas 1 and 2, the refrigerant can be surely stirred and mixed.
Further, if the shape of the branch space 5 is configured to satisfy the equations 3 and 4, the gas-liquid two-phase refrigerant in a homogeneous state flows out from the outflow pipes 3a and 3b, respectively, and the performance as the refrigerant distributor is maintained. it can.

Although an example having two outflow pipes 3a and 3b has been described with reference to FIGS. 3 and 4, the same effect can be obtained even when the number of outflow pipes is three or more. The shape of the branch space 5 may be any shape such as a cylindrical shape or a saddle shape, and the height H may be configured to satisfy the expression 3 and the volume V may be configured to satisfy the expression 4. Good. Further, even if neither Expression 3 nor Expression 4 is satisfied, if either the height H or the volume V is satisfied, the effect of uniformly distributing the gas-liquid two-phase refrigerant is exhibited to some extent.

In the above description, the example in which the gas-liquid two-phase refrigerant flows into the refrigerant distributor has been described. However, the gas-liquid single-phase refrigerant, the gas-liquid two-phase refrigerant flowing by mixing the gas refrigerant and the refrigerating machine oil, and the like. , Liquid refrigerant and liquid-liquid refrigerant in which the refrigerating machine oil that does not dissolve in the refrigerant flows, the same also in the state such as gas-liquid-liquid refrigerant that flows in the refrigerating machine oil and gas refrigerant that do not dissolve in the liquid refrigerant and refrigerant, the mixing portion is a thin tube, In particular, if it is configured so as to satisfy Equations 1 and 2,
The refrigerant distributor exerts an effect of uniformly distributing the refrigerant. Further, if the branch space 5 is configured to satisfy the formulas 3 and 4, the refrigerant can be distributed more uniformly.

Embodiment 2. Hereinafter, a refrigerant distributor according to the second embodiment of the present invention will be described. FIG. 9 is a perspective view showing the refrigerant distributor according to the present embodiment. In the figure, 6 is a stirring means for stirring the refrigerant in the mixing part 4 and the branch space 5, for example, a vibrating element such as an ultrasonic self-exciting element or an electromagnetic vibrating element that oscillates when energized from the outside. It is attached to a portion corresponding to the branch space 5 outside the unit 1.

In this embodiment, the vibrating element 6 vibrates the mixing section 4 and the branch space 5 from the outside of the refrigerant distributor body 1 to stir and mix the refrigerant inside. Therefore, the effect of agitating and mixing the gas-liquid two-phase refrigerant in the mixing section 4 and the branch space 5 is made more reliable, and the effect of distributing the refrigerant more uniformly is exhibited. Even if a stirring device such as a stirring impeller rotated by using a motor or a stirring impeller rotated by a refrigerant flow is provided in the branch space 5 in the refrigerant distributor main body 1 as the stirring means, the same effect can be obtained. Play.

Embodiment 3. Hereinafter, a refrigerant distributor according to the third embodiment of the present invention will be described. FIG. 10 is a refrigerant circuit diagram showing a refrigeration cycle device such as an air conditioner or a refrigeration device using the refrigerant distributor according to the present embodiment. In the figure, 1 is a refrigerant distributor, 7 is a compressor, 8 is a condenser, and 9
Is an expansion valve and 10 is an evaporator.

In the refrigeration cycle apparatus having such a configuration, the refrigerant flow path between the expansion valve 9 and the evaporator 10 divides the circulating refrigerant into a plurality of, in this case, three paths.
Therefore, the refrigerant distributor 1 described in the first or second embodiment is arranged at this branch portion. Where mass flow rate W
To change [kg / s], for example, the rotation speed of the compressor 7 or the opening degree of the expansion valve 9 may be changed. By using this refrigerant distributor, the refrigerant can be evenly distributed in the three paths to the evaporator 10, and the performance and efficiency of the refrigeration cycle apparatus can be improved.

In general, refrigerant noise is likely to occur in a gas-liquid two-phase flow. It is considered that the cause of this refrigerant noise is that a nonuniform liquid droplet flow collides with the tube wall. For example, in a refrigeration cycle device incorporating a refrigerant distributor in which a refrigerant circulates as a non-homogeneous flow, the refrigerant noise may be offensive to the ear and may be cited as one of the causes of defects. Therefore, in the present embodiment, when the refrigeration cycle device is configured, as shown in FIG. 10, the mixing portion and the branch space configured by thin tubes are optimally configured by using the mass flow rate of the refrigerant, and the gas-liquid two-phase refrigerant is used. The use of a refrigerant distributor capable of achieving homogenization of the refrigerant makes it possible to prevent the generation of refrigerant noise in the refrigeration cycle apparatus. As described above, in the present embodiment, the refrigerant is homogeneously distributed to improve the performance and efficiency of the refrigeration cycle apparatus, and the reliability problem due to the inhomogeneity of the refrigerant distribution, for example, the generation or evaporation of the refrigerant noise. It also has the effect of preventing dew splashing on the vessel.

FIG. 11 shows a plurality of indoor units 1
1 shows a multi-type air conditioner in which an outdoor unit 12 and an outdoor unit 12 are connected in parallel, in which a refrigerant distributor according to the first or second embodiment is used in a portion for distributing a refrigerant from a main refrigerant passage to each unit. It is a refrigerant circuit diagram. In the figure, 11a is a heat exchanger of the indoor unit 11, and 12a is a heat exchanger of the outdoor unit 12. In this embodiment,
The refrigerant distributor 1 is disposed at two locations, a location branching into a plurality of indoor units 11 and a refrigerant flow channel branching into a plurality of outdoor units 12. The refrigerant distributor according to the first or second embodiment exerts an effect of uniformly distributing the refrigerant to each of the indoor unit 11 and the outdoor unit 12, improves the performance and efficiency of the air conditioner, and generates the refrigerant noise. It also has the effect of preventing dew splash on the evaporator. In addition, in the above multi-type air conditioner, the two refrigerant distributors 1 are provided in the branch portion, but in this circuit configuration,
Since the refrigerant in the portion flowing into the indoor unit 11 is not in the gas-liquid two-phase state, the state of the circulating refrigerant does not change so much even if the refrigerant distributor at this branch portion is omitted.

Fourth Embodiment Hereinafter, a refrigerant distributor according to the fourth embodiment of the present invention will be described. 12 is shown in FIG.
In the refrigerant distributor having the same structure as the above, it is a characteristic diagram showing the test results for examining the flow state of the refrigerant flowing into the mixing section 4 in a gas-liquid two-phase state by changing the size of each part, the gas-liquid flow rate ratio, and the like. . The vertical axis and the horizontal axis of FIG. 12 are values representing the flow state of the refrigerant, and the vertical axis is Gg / λ, which indicates the mass flow rate of the refrigerant, and the value increases as it goes up. Also,
The horizontal axis represents λ × ψ × Gl / Gg, which represents the ratio of the gas mass flow rate to the liquid mass flow rate of the refrigerant, that is, the dryness. The dryness decreases toward the right and becomes liquid-rich. However, each parameter in the above equation represents the following. λ = [(ρg / ρa) × (ρl / ρw)] ^1/2 ψ = (σw / σ) × [(μl / μw) × (ρw / ρl)
² ] ^1/3 Gg [kg / m ² · h]: Gas refrigerant mass flow rate Gl [kg / m ² · h]: Liquid refrigerant mass flow rate ρ: Density σ: Surface tension μ: Viscosity coefficient subscript g, l , A, and w represent gas, liquid, air, and water, respectively.

The flow state of the refrigerant shown in FIG. 12 will be described below with reference to FIG. In FIG. 13, (a) stratified flow,
Flow states called (b) wavy flow and (c) slug flow are
This is an example in which the gas-liquid two-phase refrigerant has a large uneven flow.
The flow states called (e) bubbly flow and (f) annular spray flow are a state in which a gas-liquid two-phase refrigerant is mixed and stirred. Figure 1
In the graph shown in FIG. 2, the regions showing the flow state of the refrigerant are divided according to the values on the vertical axis and the horizontal axis. Here, FIG. 14 shows the test results of examining the refrigerant distribution ratio in the outflow pipe under the conditions of the points indicated by the black circles and the points indicated by the white circles in FIG. Figure 1
4 is intended for the refrigerant distributor having the configuration shown in FIG. 4, the vertical axis represents the refrigerant distribution ratio of the lower outflow pipe 3a, and the horizontal axis represents λ × ψ × Gl.
7 is a graph showing / Gg. In FIG. 14, the practical allowable range that does not cause the performance deterioration due to the distribution ratio of the two outflow pipes is set to 48% to 52%, and is shown within the range of the diagonal lines.
As is clear from the figure, under the conditions of black circles, all are within the allowable range, and under the conditions of white circles, all are outside the allowable range. Considering together with FIG. 12 and FIG. 13, it can be seen that a good refrigerant distribution result can be obtained in the state of the annular spray flow and the bubbly flow in the mixing section.

Therefore, as is apparent from FIG. 12, when the gas-liquid two-phase refrigerant at the inlet of the mixing section 4 is in the range satisfying the expressions 5 and 6, the state of the bubbly flow to the annular spray flow is changed in the mixing section. can get. Gg / λ> 5 × 10 ⁴ (5) λ × ψ × Gl / Gg> 20 (6) Then, by configuring the mass flow rate of the refrigerant so as to satisfy Equations 5 and 6, The flow state of the refrigerant in the mixing section 4 becomes a state of being mixed and agitated, and is homogenized without any drift.
Therefore, the refrigerant in a homogeneous state flows out from the outflow pipe, and the performance as the refrigerant distributor can be maintained.

Further, the refrigerant distributor according to the present embodiment is
The flow state of the gas-liquid two-phase refrigerant at the inlet of the mixing section 4 is Gg / λ
> 5 × 10 ⁴ and λ × ψ × Gl / Gg> 20 Since the gas-liquid two-phase refrigerant can be homogenized only within the range shown, the refrigerant noise generated due to the refrigerant circulating as an inhomogeneous flow is also generated. You can prevent it.

Although the refrigerant distributor having the two outflow pipes 3a and 3b has been described here, even when the number of the outflow pipes is three or more, the gas-liquid two-phase refrigerant at the inlet of the mixing section 4 is expressed by the formula 5 ，
If it is limited to the range that satisfies Expression 6, the refrigerant distributor exerts the effect of uniformly distributing the refrigerant.

Further, the refrigerant distributor according to the present embodiment is
As shown in the second embodiment, by providing a stirring means by a vibrating element outside the refrigerant distributor main body 1 or by providing a stirring means in the branch space 5 in the refrigerant distributor main body 1,
The effect of stirring and mixing the gas-liquid two-phase refrigerant in the mixing section 4 and the branch space 5 is further ensured, and the effect of uniformly distributing the refrigerant is exhibited.

Further, the refrigerant distributor according to the present embodiment is
As shown in the third embodiment, in a refrigeration cycle device such as an air conditioner or a refrigeration device, when the internal refrigerant flow passage is divided into a plurality of paths by a heat exchanger acting as a condenser or an evaporator, heat exchange is performed. It may be used in a branch portion that distributes the refrigerant to each path at the inlet of the vessel. Further, in a multi-type air conditioner in which a plurality of outdoor units and indoor units are connected in parallel, it may be used as a branch portion for distributing a refrigerant from a main refrigerant passage to each unit. By using such a refrigeration cycle device, it exerts the effect of uniformly distributing the refrigerant, improves the performance and efficiency of the refrigeration cycle device, and has a reliability problem due to the non-uniformity of the refrigerant distribution, for example, It also has the effect of preventing the generation of refrigerant noise and the exposure of the evaporator to dew.

In addition, the refrigerant distributor described in the first to fourth embodiments is, for example, H when the kind of the refrigerant is changed.
CFC refrigerants (including R22, single refrigerant, mixed refrigerant)
And HFC refrigerants (R134a, R407C, R410
A, R404A, etc., including single and mixed refrigerants), HC
System refrigerants (including methane, ethane, propane, butane, isobutane, etc., single refrigerant and mixed refrigerant) and other natural refrigerants (air, water, carbon dioxide, etc., single refrigerant, mixed refrigerant)
The same applies to the mixed refrigerant of the above-mentioned refrigerants, and the effect of uniformly distributing the refrigerants is exhibited.

Further, the refrigerant distributors according to the first to fourth embodiments are installed regardless of the installation location, for example, in the unit of an air conditioner or a refrigerating apparatus or outside the unit. Also has the same effect. Further, for example, in the first to fourth embodiments, the case where the refrigerant distributor is arranged horizontally has been described. However, when the refrigerant distributor is arranged vertically, or when it is arranged at a slight inclination from the vertical, the refrigerant distributor is arranged. The effect of uniformly distributing the refrigerant is exhibited regardless of the arrangement state of.

In the refrigerant distributor described in the first to fourth embodiments, if the inner diameter of the inflow pipe 2 is a thin tube similar to the inner diameter of the mixing part 4, the mixing part is mixed in the inflow pipe 2. The function of 4 can be substituted, and the effect of uniformly distributing the refrigerant is exhibited.

Further, assuming that the refrigerant distributor according to the first embodiment and the refrigerant distributor according to the fourth embodiment are combined, the values of the respective parts shown in FIG. 1 are L / D> 5, W / (π ×
^{D 2/4)> 500 (} π: circular constant), W / H> 2, and W / V> limited to the range indicated in 10, and the flow state of the gas-liquid two-phase refrigerant at the inlet of the mixing section 4 Gg / λ> 5 × 10 ⁴
And λ × ψ × Gl / Gg> 20, the effect of more evenly distributing the refrigerant is exhibited. In addition, by using this refrigerant distributor in a refrigeration cycle device, performance and efficiency are improved, and reliability problems due to inhomogeneity of refrigerant distribution, such as generation of refrigerant noise and exposure of the evaporator It also has the effect of preventing such problems.

[0046]

As described above, according to the first aspect of the present invention, the refrigerant flowing from the inflow pipe is connected to the mixing portion and the plurality of outflow pipes, and the refrigerant flowing from the mixing portion is discharged from the outflow pipe. includes a branch space distribution respectively, contact the mixing unit
Inner diameter is D [m], and the length in the flow direction of the refrigerant is L
[M], the mass flow rate of the refrigerant flowing through this mixing section is W [kg
/ S], D and L satisfy L / D> 5.
A, D, W is ^{W / (π × D 2/} 4)> 500 (π: circle
Since the mixing section is configured to satisfy the above condition, the refrigerant is agitated and mixed without being affected by uneven flow without separation of gas and liquid regardless of the installation status of the refrigerant distributor, and the refrigerant is distributed homogeneously. There is an effect that a refrigerant distributor that can be obtained is obtained.

[0047]

[0048]

[0049]

According to a second aspect of the present invention, in the refrigerant distributor according to the first aspect, the height of the branch space in the flow direction of the refrigerant is H [m], and the mass flow rate of the refrigerant flowing through the mixing section. Is W [kg / s], the branch space is configured so as to satisfy W / H> 2, so that gas-liquid separation occurs without being affected by uneven flow regardless of the installation status of the refrigerant distributor. It is possible to obtain a refrigerant distributor that can stir and mix the refrigerant without any need and can evenly distribute the refrigerant.

According to a third aspect of the present invention, in the refrigerant distributor according to the first or second aspect , the volume of the branch space is V [m ³ ] and the mass flow rate of the refrigerant flowing through the mixing section is If W [kg / s] is set, the branch space is configured so as to satisfy W / V> 10, so that gas-liquid separation occurs without being affected by uneven flow regardless of the installation status of the refrigerant distributor. There is an effect that a refrigerant distributor that can stir and mix the refrigerant without the need to uniformly distribute the refrigerant can be obtained.

[0052]

Further, according to a fourth aspect of the present invention, by providing the refrigerant distributor according to any one of the first to third aspects in a refrigerant branch portion of a refrigerant passage for circulating a refrigerant, An effect that can improve the performance and efficiency of the refrigeration cycle device, and can also provide a refrigeration cycle device that can prevent reliability problems due to inhomogeneity of refrigerant distribution, for example, generation of refrigerant noise and dew splash in the evaporator There is.

[Brief description of drawings]

FIG. 1 is a sectional view showing a refrigerant distributor according to a first embodiment of the present invention.

FIG. 2 is an explanatory diagram showing a state of a refrigerant in a refrigerant distributor body according to the first embodiment.

FIG. 3 is a perspective view showing a refrigerant distributor in the case where two outflow pipes are horizontally installed according to the first embodiment.

FIG. 4 is a perspective view showing a refrigerant distributor when two outflow pipes are installed in a vertical direction according to the first embodiment.

FIG. 5 relates to the first embodiment, where the inner diameter of the mixing portion is D
It is a graph which shows the relationship between L / D and a distribution ratio when [m] and length are L [m].

FIG. 6 is a graph showing a relationship between a mass flow rate W [kg / s] of a refrigerant flowing through a mixing section and a distribution ratio according to the first embodiment.

FIG. 7 relates to the first embodiment and sets the height of a branch space to H.
6 is a graph showing the relationship between W / H and the distribution ratio, where [m] is the inner diameter of the mixing section, D [m], and the mass flow rate W [kg / s] of the refrigerant flowing through the mixing section.

FIG. 8 relates to the first embodiment and sets the height of the branch space to H.
[M], the volume is V [m ³ ], the inner diameter of the mixing section is D [m],
It is a graph which shows the relationship of W / V and distribution ratio when it is considered as the mass flow rate W [kg / s] of the refrigerant which flows through a mixing part.

FIG. 9 is a perspective view showing a refrigerant distributor according to a second embodiment of the present invention.

FIG. 10 is a refrigerant circuit diagram of a refrigeration cycle device using a refrigerant distributor according to a third embodiment of the present invention.

FIG. 11 is a refrigerant circuit diagram of a multi-type air conditioner using the refrigerant distributor according to the third embodiment.

FIG. 12 is a characteristic diagram showing a flow state of the gas-liquid two-phase refrigerant at the inlet of the mixing section in the refrigerant distributor according to the fourth embodiment of the present invention.

FIG. 13 is a diagram showing a refrigerant distributor according to a fourth embodiment,
It is explanatory drawing showing the flow mode of a gas-liquid two-phase refrigerant.

FIG. 14 relates to a fourth embodiment and is in a fluidized state λ × ψ × G.
It is a graph which shows the relationship between l / Gg and a distribution ratio.

FIG. 15 is a cross-sectional view showing a conventional refrigerant distributor.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Refrigerant distributor main body, 2 Inflow pipe, 3a, 3b Outflow pipe, 4 Mixing part, 5 Branch space, 6 Stirring means, 7 Compressor, 8 Condenser, 9 Expansion valve, 10 Evaporator, 11
Outdoor unit, 12 indoor units.

─────────────────────────────────────────────────── ─── Continued Front Page (72) Inventor Tomohiko Kasai 2-3-3 Marunouchi, Chiyoda-ku, Tokyo Mitsubishi Electric Corporation (72) Inventor Isao Funayama 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsubishi Electric Co., Ltd. (72) Inventor Kunihiro Morishita 2-3-3 Marunouchi, Chiyoda-ku, Tokyo Mitsubishi Electric Co., Ltd. (56) Reference JP-A-6-88657 (JP, A) Actual Development Sho 54-42155 (JP , U) (58) Fields investigated (Int.Cl. ⁷ , DB name) F25B 41/00

Claims (4)

(57) [Claims] 1. A mixing unit for passing the refrigerant flowing in from the inlet pipe, and connected to a plurality of outlet tubes, the refrigerant flowing from the mixing section comprises a branch space to be distributed to each of the outflow pipe, the mixed Inner diameter of the part is D [m], refrigerant
The length in the flow direction of L [m], the refrigerant flowing through this mixing section
If the mass flow rate of W is [kg / s], then D and L are L /
While satisfying D> 5, D and W are W / (π × D ² /
4) The above-mentioned mixing part so as to satisfy> 500 (π: pi)
Refrigerant distributor characterized in that. 2. The height of the branch space in the flow direction of the refrigerant is H
[M], the mass flow rate of the refrigerant flowing through the mixing section is W [kg /
[s]], the refrigerant distributor according to claim 1 , wherein the branch space is configured so as to satisfy W / H> 2. 3. When the volume of the branch space is V [m ³ ] and the mass flow rate of the refrigerant flowing through the mixing section is W [kg / s], W /
The refrigerant distributor according to claim 1 or 2 , wherein the branch space is configured to satisfy V> 10. 4. A refrigerant distributor and a refrigeration cycle device, characterized in that provided in the refrigerant branch portion of the refrigerant flow path for circulating a refrigerant according to any one of claims 1 to 3.