JP3216469B2 - Evaporator for air conditioner - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an evaporator for an air conditioner, and more particularly, to an air conditioner having a plurality of refrigerant distribution systems and capable of equally distributing the refrigerant flowing through each refrigerant distribution system. The present invention relates to a mechanical evaporator.

[0002]

2. Description of the Related Art An evaporator for an air conditioner having a plurality of refrigerant distribution systems is well known in the art, and the distribution of refrigerant to each refrigerant distribution system is performed on the inlet side of the evaporator. However, the flow pattern of the refrigerant before the split on the inlet side of the evaporator is a gas-liquid two-phase flow,
When the refrigerant distribution system is used in a horizontal posture, the gas refrigerant tends to be biased vertically upward and the liquid refrigerant tends to be biased downward due to the influence of gravity. In the case of such a gas-liquid two-phase flow, the state of the refrigerant in each refrigerant distribution system (that is, the gas-liquid ratio) is obtained simply by branching the refrigerant into the refrigerant distribution system at the evaporator inlet side.
(Ie, refrigerant drift occurs), and there is a problem that the heat exchange performance cannot be sufficiently obtained.

Therefore, a flow divider is connected to the inlet side of the evaporator, and a member for guiding the refrigerant spirally is provided on the inner surface of the refrigerant pipe on the upstream side of the flow divider, and a uniform state is provided to each refrigerant distribution system. A technique for diverting the refrigerant is employed (for example, see Japanese Utility Model Laid-Open No. 57-5683).

[0004]

However, even when the refrigerant on the inlet side of the flow divider is spirally rotated as in the above-mentioned known example, each refrigerant is uniformly mixed with the refrigerant in the two-phase flow state. It is difficult to evenly distribute the refrigerant to the refrigerant distribution system, and this has been a cause of hindering the improvement of the heat exchange performance of the evaporator for the air conditioner.

[0005] The present invention has been made in view of the above points, and has as its object to improve the heat exchange performance by preventing the refrigerant from drifting in each refrigerant distribution system.

[0006]

According to a first basic configuration of the present invention, as an means for solving the above-mentioned problems, an air conditioner configured so that refrigerant can be divided into a plurality of refrigerant distribution systems 2A and 2B. In the mechanical evaporator, the refrigerant gas immediately before the branch is bypassed to the outlet pipe 3 of the evaporator via the gas vent pipe 4.

In the first basic configuration of the present invention, the outlet of the degassing pipe 4 is connected to the outlet side of the refrigerant flow system 2B having a smaller dryness among the refrigerant flow systems 2A and 2B. This is preferable in that the drift of the refrigerant in 2A and 2B can be more effectively prevented.

A control valve 5 for controlling the flow rate of the refrigerant gas is provided in the degassing pipe 4 and refrigerant temperature detecting means 6 for detecting the outlet refrigerant temperature in each of the refrigerant distribution systems 2A and 2B. 7 and control means 21 for controlling the opening of the control valve 5 so that the refrigerant temperatures detected by the respective refrigerant temperature detecting means 6 and 7 become equal. Each refrigerant distribution system 2A,
This is preferable in that the refrigerant can be evenly divided into 2B evenly.

In addition, a control valve 5 for controlling the flow rate of the refrigerant gas is provided in the degassing pipe 4, and the refrigerant distribution system 2 having a large dryness among the refrigerant distribution systems 2A and 2B is provided.
A, the refrigerant temperature detecting means 6, 8 for detecting the outlet refrigerant temperature and the intermediate refrigerant temperature, respectively, and the opening of the control valve 5 so that the refrigerant temperatures detected by the respective refrigerant temperature detecting means 6, 8 become equal. The control means 21 for performing the control is additionally provided by controlling the degree of opening of the control valve 5 so that each refrigerant flow system 2A,
This is preferable in that the refrigerant can be evenly divided into 2B evenly.

In a second basic configuration of the present invention, as a means for solving the above-mentioned problems, a plurality of refrigerant distribution systems 2 are provided.
In the evaporator for an air conditioner configured so that the refrigerant can be divided into the refrigerants A and 2B, the liquid refrigerant immediately before the division is flowed through the drain pipe 9 into the refrigerant circulation systems 2A and 2B, where the refrigerant having a large degree of dryness flows. It is bypassed to the outlet side in the system 2A.

In the second basic configuration of the present invention, a control valve 10 for controlling the flow rate of the liquid refrigerant is interposed in the liquid drain pipe 9 and the outlet refrigerant temperature in each of the refrigerant flow systems 2A and 2B is controlled. The refrigerant temperature detecting means 6 and 7 to be detected and the control means 21 for controlling the opening degree of the control valve 10 so that the refrigerant temperatures detected by the respective refrigerant temperature detecting means 6 and 7 are equal to each other. This is preferable in that the opening of the control valve 10 can be controlled so that the refrigerant can be evenly divided equally into each of the refrigerant flow systems 2A and 2B.

A control valve 10 for adjusting the flow rate of the liquid refrigerant is provided in the liquid drain pipe 9 and the refrigerant flow system 2A having a large dryness among the refrigerant flow systems 2A and 2B.
, And the opening degree control of the control valve 10 so that the refrigerant temperatures detected by the respective refrigerant temperature detecting means 6, 8 become equal. And a control means 21 for controlling each refrigerant flow system 2 by controlling the opening degree of the control valve 10.
This is preferable because the refrigerant can be evenly divided equally into A and 2B.

Further, the control valve 10 in the drain pipe 9
Control valve 1 for attaching a bypass pipe 11 for connecting the downstream side of the liquid refrigerant to the liquid phase portion on the outlet side of the refrigerant flow system 2B having a low degree of dryness, and adjusting the flow rate of the liquid refrigerant to the bypass pipe 11
2 and the respective refrigerant distribution systems 2A, 2B
And a first control unit for controlling the opening degree of the bypass control valve 12 so that the refrigerant temperatures detected by the refrigerant temperature detection units 6 and 7 become equal. Control means 21A and the first
When the opening degree control by the control means 21A becomes impossible, the control valve is controlled so that the refrigerant temperatures detected by the refrigerant temperature detecting means 6, 7 under the condition that the bypass control valve 12 is closed become equal. The second control means 21B for controlling the opening degree of the valve 10 is provided so that the control of the opening degree of the control valve 10 and the bypass control valve 12 allows the refrigerant to be evenly divided into the respective refrigerant circulation systems 2A and 2B. It is preferable because it can be performed.

The control valve 10 in the drain pipe 9
Control valve 1 for attaching a bypass pipe 11 for connecting the downstream side of the liquid refrigerant to the liquid phase portion on the outlet side of the refrigerant flow system 2B having a low degree of dryness, and adjusting the flow rate of the liquid refrigerant to the bypass pipe 11
And refrigerant temperature detecting means 6, 8 for detecting the outlet refrigerant temperature and the intermediate refrigerant temperature in the refrigerant distribution system 2A having a large degree of dryness among the refrigerant distribution systems 2A and 2B. First control means 21A for controlling the opening degree of the bypass control valve 12 so that the refrigerant temperatures detected by the detection means 6 and 8 become equal;
When the opening degree control by the control means 21A becomes impossible, the control valve is controlled so that the refrigerant temperatures detected by the refrigerant temperature detecting means 6, 8 become equal under the condition that the bypass control valve 12 is closed. The second control means 21B for controlling the opening degree of the valve 10 is provided so that the control of the opening degree of the control valve 10 and the bypass control valve 12 allows the refrigerant to be evenly divided into the respective refrigerant circulation systems 2A and 2B. It is preferable because it can be performed.

[0015]

According to the first basic configuration of the present invention, the following effects can be obtained by the above means.

That is, by bypassing the gas refrigerant of the refrigerant in the gas-liquid two-phase flow state before the branch to the outlet pipe 3 in the evaporator, the ratio of the liquid refrigerant in the refrigerant before the branch is greatly increased. (In other words, almost only the liquid refrigerant), and the refrigerant is equally distributed to the refrigerant distribution systems 2A and 2B.

In the first basic configuration of the present invention, when the outlet of the degassing pipe 4 is connected to the outlet side of the refrigerant flow system 2B having a low degree of dryness among the refrigerant flow systems 2A and 2B, the flow before the flow is divided. The ratio of the liquid refrigerant in the refrigerant is greatly increased, and each refrigerant distribution system 2A, 2A
A uniform distribution of the refrigerant to B is obtained, and the refrigerant flow to the outlet side of the refrigerant distribution system 2B having a smaller dryness is more effectively prevented from flowing in the refrigerant distribution systems 2A and 2B.

In addition, a control valve 5 for controlling the flow rate of the refrigerant gas is interposed in the degassing pipe 4, and refrigerant temperature detecting means 6 for detecting the outlet refrigerant temperature in each of the refrigerant distribution systems 2A and 2B, respectively. 7 and control means 21 for controlling the opening of the control valve 5 so that the refrigerant temperatures detected by the refrigerant temperature detecting means 6 and 7 become equal, or the gas vent pipe 4 is provided with: A control valve 5 for adjusting the flow rate of the refrigerant gas is interposed, and the refrigerant distribution system 2A having a large dryness among the refrigerant distribution systems 2A and 2B.
And the opening degree control of the control valve 5 such that the refrigerant temperatures detected by the respective refrigerant temperature detecting means 6 and 8 become equal. When the control means 21 is provided, the equalization of the refrigerant circulation state in each of the refrigerant circulation systems 2A and 2B can be obtained by controlling the opening degree of the control valve 5, so that the refrigerant flowing to each of the refrigerant circulation systems 2A and 2B is Even distribution can be performed more appropriately.

In the second basic configuration of the present invention, the following effects can be obtained by the above means.

That is, by bypassing the liquid refrigerant among the refrigerants in the gas-liquid two-phase flow state before the branching to the outlet side of the refrigerant circulation system 2A having the greater dryness among the refrigerant circulation systems 2A and 2B, each refrigerant circulation Dryness in the systems 2A and 2B is equalized, and as a result, equal distribution of the refrigerant in each of the refrigerant distribution systems 2A and 2B is obtained.

In the second basic configuration of the present invention, a control valve 10 for controlling the flow rate of the liquid refrigerant is interposed in the liquid drain pipe 9 and the outlet refrigerant temperature in each of the refrigerant flow systems 2A and 2B is controlled. When the refrigerant temperature detecting means 6 and 7 to be detected and the control means 21 for controlling the opening degree of the control valve 10 so that the refrigerant temperatures detected by the respective refrigerant temperature detecting means 6 and 7 become equal, Alternatively, a control valve 10 for adjusting the flow rate of the liquid refrigerant is interposed in the liquid drain pipe 9, and the outlet refrigerant temperature, the intermediate refrigerant temperature, and the outlet refrigerant temperature in the refrigerant flow system 2A having a large dryness among the refrigerant flow systems 2A and 2B. Temperature detecting means 6, 8 for detecting the temperature of the refrigerant, and control means 21 for controlling the opening degree of the control valve 10 so that the refrigerant temperatures detected by the respective refrigerant temperature detecting means 6, 8 become equal. If it annexed to, equalization adjustment valve of the refrigerant flow states in each refrigerant flow lines 2A, 2B 1
Since it can be obtained by the opening degree control of 0, the refrigerant can be evenly distributed to the respective refrigerant distribution systems 2A and 2B more appropriately.

The control valve 10 in the drain pipe 9
Control valve 1 for attaching a bypass pipe 11 for connecting the downstream side of the liquid refrigerant to the liquid phase portion on the outlet side of the refrigerant flow system 2B having a low degree of dryness, and adjusting the flow rate of the liquid refrigerant to the bypass pipe 11
2 and the respective refrigerant distribution systems 2A, 2B
And a first control unit for controlling the opening degree of the bypass control valve 12 so that the refrigerant temperatures detected by the refrigerant temperature detection units 6 and 7 become equal. Control means 21A and the first
When the opening degree control by the control means 21A becomes impossible, the control valve is controlled so that the refrigerant temperatures detected by the refrigerant temperature detecting means 6, 7 under the condition that the bypass control valve 12 is closed become equal. In the case where a second control means 21B for controlling the opening degree of 10 is provided, or the downstream side of the control valve 10 in the liquid drain pipe 9 and the liquid phase portion on the outlet side of the refrigerant flow system 2B having a small dryness are connected. A bypass pipe 11 to be connected is provided and a bypass control valve 12 for adjusting the flow rate of the liquid refrigerant is interposed in the bypass pipe 11, and an outlet in the refrigerant distribution system 2A of the refrigerant distribution systems 2A and 2B having a large dryness. The refrigerant temperature detecting means 6 and 8 for detecting the refrigerant temperature and the intermediate refrigerant temperature, respectively, and the refrigerant temperatures detected by the refrigerant temperature detecting means 6 and 8 are equalized. First control means 21A for controlling the opening degree of the bypass control valve 12; and each of the above-mentioned control means in a state in which the bypass control valve 12 is closed when the opening control by the first control means 21A becomes impossible. Second control means 2 for controlling the opening degree of the control valve 10 so that the refrigerant temperatures detected by the refrigerant temperature detection means 6, 8 become equal.
1B, even if the dryness in each of the refrigerant flow systems 2A and 2B differs due to refrigerant drift, the refrigerant flow state in each of the refrigerant flow systems 2A and 2B is controlled by controlling the opening of the control valve 10 and the bypass control valve 12. Can be obtained.

[0023]

According to the first basic configuration of the present invention, of the refrigerant in the gas-liquid two-phase flow state before the branch, the gas refrigerant is bypassed to the outlet pipe 3 in the evaporator, so that the refrigerant before the branch is separated. Since the ratio of the liquid refrigerant is greatly increased, the refrigerant can be evenly distributed to the refrigerant distribution systems 2A and 2B, and the heat exchange performance in the refrigerant distribution systems 2A and 2B can be fully utilized. There is an excellent effect that it becomes possible.

According to the second basic configuration of the present invention, the liquid refrigerant among the refrigerants in the gas-liquid two-phase flow state before the branch is divided into the refrigerant distribution system 2A having a large dryness among the refrigerant distribution systems 2A and 2B.
In each refrigerant distribution system 2
A and 2B equalized the degree of dryness,
An even distribution of the refrigerant in each of the refrigerant distribution systems 2A and 2B can be obtained, and there is an excellent effect that the heat exchange performance in each of the refrigerant distribution systems 2A and 2B can be drawn to its full capacity.

[0025]

Preferred embodiments of the present invention will be described below with reference to the accompanying drawings.

First Embodiment FIGS. 1 and 2 show an air conditioner evaporator according to a first embodiment of the present invention.

As shown in FIG. 1, the evaporator for an air conditioner of the present embodiment has two refrigerant circulation systems 2A and 2B branched from an inlet pipe 1 connected to an expansion mechanism (not shown). The refrigerant flow systems 2A and 2B are joined to an outlet pipe 3 connected to a compressor (not shown) on the outlet side. And a gas phase portion 1a in the inlet pipe 1.
The outlet pipe 3 is communicated with the outlet pipe 3 through a vent pipe 4, and the gas refrigerant X ₁ of the gas-liquid two-phase refrigerant X flowing through the inlet pipe 3 is connected to the outlet pipe via the vent pipe 4. 3
It is to be bypassed to. Note that the refrigerant flow systems 2A and 2B are branched in the vertical direction. Sign 1
b is a liquid phase part.

In the evaporator for an air conditioner configured as described above, the following operation is obtained.

The refrigerant X that has been depressurized in the expansion mechanism flows through the inlet pipe 1 is a gas-liquid two-phase flow, but in the present embodiment, the gas refrigerant X ₁ of the gas-liquid two-phase flow is vented has become possible is caused to pass to the outlet pipe 3 through the tube 4, as shown in FIG. 2, the only little liquid refrigerant X ₂ is drawn off the gas refrigerant X ₁ in the inlet pipe 1. Therefore, the distribution of the refrigerant to the refrigerant distribution systems 2A and 2B can be performed evenly. As a result, the refrigerant distribution system 2
A and 2B eliminate the refrigerant drift, and the refrigerant distribution system 2
The heat exchange performance in A and 2B can be brought out to full capacity. In the case of this embodiment, since the gas refrigerant X ₁ in the refrigerant X flowing inlet pipe 1 has a be bypassed to the outlet pipe 3, but the flow rate of refrigerant supplied to the evaporator is reduced, specific volume is large, so bypassing gas refrigerant X ₁ which does not contribute much to the heat exchanger no problem.

Second Embodiment FIGS. 3 and 4 show an evaporator for an air conditioner according to a second embodiment of the present invention.

In the case of this embodiment, a control valve 5 for adjusting the flow rate of the refrigerant is provided in the middle of the degassing pipe 4 in the first embodiment. Each refrigerant flow line 2A, to the outlet side of 2B, a thermistor 6 and 7 acts as a refrigerant temperature detecting means for detecting each of the outlet refrigerant temperature T _1, T ₂ is attached. Reference numeral 8 denotes a thermistor which is an existing refrigerant temperature detecting means for detecting an intermediate refrigerant temperature in order to obtain a degree of superheating in the evaporator.

As shown in FIG. 4, the output signals from the thermistors 6 and 7 are supplied to a control means 21 having a temperature difference calculator 22, an opening calculator 23 and an opening output unit 24.
The thermistors 6, 7
Calculation of the temperature difference ΔT ₁ = T ₁ -T ₂ is performed by the temperature difference calculation section 22 based on an output signal from the temperature difference calculating unit 2
2 based on the temperature difference ΔT ₁ obtained in Step 2
3, the degree of opening of the control valve 5 is determined. The opening calculated by the opening calculating section 23 is output to an opening output section 24, and the opening of the control valve 5 is controlled so that ΔT ₁ ≒ 0 by a command from the opening output section 24. .

Next, the control of the opening of the control valve in the evaporator for an air conditioner of this embodiment will be described with reference to the flowchart shown in FIG.

[0034] are temporarily closed control valve 5 in Step S _1, the signal from the thermistor 6 at step S ₂ (i.e., the detected temperature T _1, T ₂₎ is input to the control means 21, the temperature in step S ₃ The difference ΔT ₁ = T ₁ −T ₂ is determined. Thereafter, the sign determination of the temperature difference [Delta] T ₁ in step S ₄ (i.e., the determination of [Delta] T _1> 0 or [Delta] T ₁ ≒ 0)
When it is determined that ΔT ₁ > 0, drift of the refrigerant occurs in the refrigerant distribution systems 2A and 2B (that is, the refrigerant flow in the refrigerant distribution system 2A is smaller than the gas refrigerant in the refrigerant distribution system 2B). since X ₁ and the ratio X ₁ / X ₂ between the liquid refrigerant X ₂ indicates a by being) that increases, by opening the regulating valve 5 by a predetermined angle in step S _5, the inlet pipe 1 in the vapor phase performing an extraction of the gas refrigerant X ₁ from 1a. Then, in the inlet pipe 1, the gas refrigerant X ₁ of the gas-liquid two-phase flow
There almost becomes only liquid refrigerant X ₂ is caused to pass to the outlet pipe 3 via the venting pipe 4, the refrigerant flow line 2
The refrigerant distribution to A and 2B can be performed evenly.

[0035] Thereafter, the control process returns to step S _2, the processing of steps S ₂ ~ Step S ₄ is performed,
Opening a result of the refrigerant even distribution according to the control valve 5 described above, if it is determined that [Delta] T ₁ ≒ 0 in step S _4, the opening degree of the regulating valve 5 in step S ₆ is maintained at the opening degree at that time. In the case where noted is determined that [Delta] T _1> 0 in step S _4, the opening degree of the regulating valve 5 in Step S ₅ is further increased.

As described above, in the present embodiment, the opening of the control valve 5 is controlled so that the refrigerant temperatures T ₁ and T _{2 at} the respective outlets of the refrigerant distribution systems 2A and 2B become substantially equal. Therefore, the refrigerant distribution systems 2A, 2B
Of the refrigerant in the refrigerant distribution systems 2A and 2B can be drawn to its full capacity. In the case of the present embodiment also, since the gas refrigerant X ₁ in the refrigerant X flowing inlet pipe 1 has a be bypassed to the outlet pipe 3, but the flow rate of refrigerant supplied to the evaporator is reduced, specific volume is large, so bypassing gas refrigerant X ₁ which does not contribute much to the heat exchanger no problem.

Third Embodiment FIG. 6 shows the contents of the control means 21 in an air conditioner evaporator according to a second embodiment of the present invention.

In the case of the present embodiment, the signals from the thermistors 6 and 8 are input to the temperature difference calculating section 22 of the control means 21, and the temperature difference ΔT ₂ between the detected temperatures T ₁ and T ₃ of the thermistors 6 and 8 = The calculation of T ₁ −T ₃ is performed, and the opening of the control valve 5 is obtained by the opening calculation unit 23 based on the temperature difference ΔT ₂ ,
The opening of the control valve 5 is controlled by a command from the opening output unit 24. The other configuration is the same as that of the second embodiment, and the description is omitted to avoid duplication.

Next, the control of the opening of the control valve in the evaporator for an air conditioner of this embodiment will be described with reference to the flowchart shown in FIG.

[0040] are temporarily closed control valve 5 in Step S _1, the signal from the thermistor 6 and 8 in step S ₂ (i.e., the detected temperature T _1, T ₃₎ is inputted to the control means 21, the temperature in step S ₃ The difference ΔT ₂ = T ₁ −T ₃ is determined. Thereafter, the sign determination of the temperature difference [Delta] T ₂ in step S ₄ (i.e., the determination of [Delta] T _2> 0 or ΔT ₂ ≒ 0)
When it is determined that ΔT ₂ > 0, drift of the refrigerant occurs in the refrigerant distribution systems 2A and 2B (that is, the refrigerant flow in the refrigerant distribution system 2A is smaller than the gas refrigerant in the refrigerant distribution system 2B). since X ₁ and the ratio X ₁ / X ₂ between the liquid refrigerant X ₂ indicates a by being) that increases, by opening the regulating valve 5 by a predetermined angle in step S _5, the inlet pipe 1 in the vapor phase performing an extraction of the gas refrigerant X ₁ from 1a. Then, in the inlet pipe 1, the gas refrigerant X ₁ of the gas-liquid two-phase flow
There almost becomes only liquid refrigerant X ₂ is caused to pass to the outlet pipe 3 via the venting pipe 4, the refrigerant flow line 2
The refrigerant distribution to A and 2B can be performed evenly.

[0041] Thereafter, the control process returns to step S _2, the processing of steps S ₂ ~ Step S ₄ is performed,
Opening a result of the refrigerant even distribution according to the control valve 5 described above, if it is determined that [Delta] T ₂ ≒ 0 in step S _4, the opening degree of the regulating valve 5 in step S ₆ is maintained at the opening degree at that time, step S changes in the refrigeration cycle at ₇ (e.g., changes such as the compressor frequency or fan speed) whether there has been is determined, the process returns to step S ₁ in the case of affirmative determination, the case of a negative determination step S ₂ Return to Incidentally, Note [Delta] T _2> 0 in step S ₄
And when it is determined, the control valve in step S ₅ 5
Is further increased.

As described above, in the present embodiment, the outlet refrigerant temperature T ₁ and the intermediate-portion refrigerant temperature T ₃ in the refrigerant distribution system 2A where the degree of dryness is large among the refrigerant distribution systems 2A and 2B.
Is controlled to make the control valve 5 almost equal to each other, so that the refrigerant drift in the refrigerant distribution systems 2A, 2B is prevented, and the refrigerant distribution systems 2A, 2A,
It is possible to bring out the heat exchange performance in 2B to full capacity.

Fourth Embodiment FIG. 8 shows an evaporator for an air conditioner according to a fourth embodiment of the present invention.

In the case of this embodiment, the outlet of the degassing pipe 4 is
The outlet side is connected to the outlet side of the refrigerant circulation system 2B having a small dryness. With this configuration, the proportion of pre-division of the refrigerant liquid in the X refrigerant X ₂ becomes possible to increase significantly, the refrigerant flow line 2A, evenly distributed along with the resulting refrigerant to 2B, the smaller of the dryness refrigerant flow line 2A supplementation gas refrigerant X ₁ to the outlet side of the refrigerant flow lines 2B, refrigerant drift to 2B can be prevented more effectively. The other configuration and operation and effect are the same as those of the first embodiment, and the description is omitted to avoid duplication.

Fifth Embodiment FIG. 9 shows an evaporator for an air conditioner according to a fifth embodiment of the present invention.

In the case of the present embodiment, a control valve 5 for adjusting the flow rate of the gas refrigerant is provided in the middle of the degassing pipe 4 in the evaporator for an air conditioner of the fourth embodiment. The control means 21 is similar to the one disclosed in the second embodiment (that is, the one shown in FIG. 4), and controls the opening degree of the control valve 5 based on input information from the thermistors 6 and 7. Has become.

Next, the control of the opening degree of the control valve in this embodiment will be described with reference to the flowchart shown in FIG.

[0048] are temporarily closed control valve 5 in Step S _1, the signal from the thermistor 6 at step S ₂ (i.e., the detected temperature T _1, T ₂₎ is input to the control means 21, the temperature in step S ₃ The difference ΔT ₁ = T ₁ −T ₂ is determined. Thereafter, the code determination (i.e. the temperature difference [Delta] T ₁ in step _{S 4, ΔT 1> 0,} ΔT 1 ≒ 0 or [Delta] T ₁
If <T0> is determined and ΔT ₁ > 0 is determined, a refrigerant drift occurs in the refrigerant distribution systems 2A and 2B (that is, the refrigerant distribution system 2A side is closer to the refrigerant distribution system 2B side). the ratio X ₁ / X ₂ between the gas refrigerant X ₁ and liquid refrigerant X ₂ compared to
It indicates that the is large), by opening the regulating valve 5 by a predetermined angle in step S _5, the gas refrigerant X ₁ from the inlet pipe 1 in the vapor phase 1a to refrigerant flow line 2B
Is performed. Then, in the inlet pipe 1, the gas refrigerant X ₁ of the gas-liquid two-phase flow is bypassed to the outlet pipe 3 via the gas vent pipe 4, and almost becomes only the liquid refrigerant X _2. , together with the refrigerant distribution to 2B are carried out uniformly, dryness of the refrigerant flow line 2B increases supplementation gas refrigerant X ₁ to refrigerant flow line 2B. That is, equal distribution of the refrigerant in the refrigerant distribution systems 2A and 2B is obtained.

[0049] Thereafter, the control process returns to step S _2, the processing of steps S ₂ ~ Step S ₄ is performed,
Opening a result of the refrigerant even distribution according to the control valve 5 described above, if it is determined that [Delta] T ₁ ≒ 0 in step S _4, although the degree of opening of the control valve 5 in Step S ₆ is maintained at the opening degree at that time, When the dryness fraction of the refrigerant flow lines 2B becomes too large due to the bypass of gas refrigerant X ₁ to refrigerant flow line 2B, it is determined that [Delta] T ₁ <0 in step S _4. At that time, the diaphragm by a predetermined amount the degree of opening of the control valve 5 in Step S _7, reducing the bypass quantity of the gas refrigerant X _1. In addition,
When the Note is determined that [Delta] T _1> 0 in step S _4, the opening degree of the regulating valve 5 in Step S ₅ is further increased.

As described above, in this embodiment, the opening degree of the control valve 5 is controlled so that the outlet refrigerant temperatures T ₁ and T ₂ of the refrigerant circulation systems 2A and 2B are substantially equal. In addition, refrigerant drift in the refrigerant distribution systems 2A and 2B is prevented, and the heat exchange performance in the refrigerant distribution systems 2A and 2B can be brought out to its full capacity.

As in the third embodiment (see FIGS. 6 and 7), the opening of the control valve 5 may be controlled based on the input information from the thermistors 6 and 8.

Embodiment 6 FIGS. 11 and 12 show an air conditioner evaporator according to Embodiment 6 of the present invention.

In the case of the present embodiment, the liquid phase portion 1b in the inlet pipe 1 and the outlet side of the refrigerant flow system 2A having a high degree of dryness in the refrigerant flow systems 2A and 2B are in a gas-liquid two-phase flow state before the split flow. It is caused to communicate with the liquid discharge tube 9 for bypassing the out liquid refrigerant X ₂ refrigerant X. The other configuration is the same as that of the first embodiment, and the description is omitted to avoid duplication.

With this configuration, the liquid refrigerant X2 among the refrigerants X in the gas-liquid two-phase flow state before the split flows is the refrigerant distribution system ₂ having a large dryness among the refrigerant distribution systems 2A and 2B.
A is bypassed to the outlet side in A, and as a result, the degree of dryness in each of the refrigerant distribution systems 2A and 2B is equalized. Accordingly, the refrigerant can be equally distributed in each of the refrigerant distribution systems 2A and 2B, and the heat exchange performance of each of the refrigerant distribution systems 2A and 2B can be fully utilized. In the case of this embodiment, the energy held by the liquid refrigerant X ₂ so as to use as a heat exchanger by a bypass to the outlet side of the large coolant flow system 2A of the dryness of the liquid refrigerant X ₂ inlet pipe 1 As a result, the refrigerant can be effectively used.

Seventh Embodiment FIGS. 13 and 14 show an evaporator for an air conditioner according to a seventh embodiment of the present invention.

In the case of the present embodiment, a control valve 10 for adjusting the flow rate of the liquid refrigerant is provided in the middle of the liquid drain pipe 9 in the evaporator for an air conditioner of the sixth embodiment. The control means 21
The signals from the thermistors 6 and 7 are to be input to the temperature difference calculating unit 22 at.
7, the temperature difference ΔT ₁ = T ₁ −T ₂ between the detected temperatures T ₁ and T ₂ is calculated. Based on the temperature difference ΔT ₁ , the opening degree of the control valve 10 is obtained by the opening degree calculation unit 23. The opening of the control valve 10 is controlled by a command from the degree output unit 24. The other configuration is the same as that of the sixth embodiment, and the description is omitted to avoid duplication.

Next, the control of the opening degree of the control valve in this embodiment will be described with reference to the flowchart shown in FIG.

[0058] are temporarily closed control valve 5 in Step S _1, the signal from the thermistor 6 at step S ₂ (i.e., the detected temperature T _1, T ₂₎ is input to the control means 21, the temperature in step S ₃ The difference ΔT ₁ = T ₁ −T ₂ is determined. Thereafter, the code determination (i.e. the temperature difference [Delta] T ₁ in step _{S 4, ΔT 1> 0,} ΔT 1 ≒ 0 or [Delta] T ₁
If <T0> is determined and ΔT ₁ > 0 is determined, a refrigerant drift occurs in the refrigerant distribution systems 2A and 2B (that is, the refrigerant distribution system 2A side is closer to the refrigerant distribution system 2B side). the ratio X ₁ / X ₂ between the gas refrigerant X ₁ and liquid refrigerant X ₂ compared to
It indicates that the is large), by opening the control valve 10 by a predetermined angle in step S _5, the liquid refrigerant X ₂ from the inlet pipe 1 of the liquid phase portion 1b to the coolant circulation system 2A
Is performed. Then, the dryness is reduced in the refrigerant circulation system 2A by a bypass of the liquid refrigerant X ₂ to the refrigerant circulation line 2A, the refrigerant flow line 2A, the outlet refrigerant temperature T ₁ of the 2B, T ₂ and are equal (i.e., refrigerant flow System 2
(A and 2B are obtained in a uniform distribution of the refrigerant).

[0059] Thereafter, the control process returns to step S _2, the processing of step S ₂ ~ step S ₄ is carried out,
As a result of equal distribution of the refrigerant by opening the control valve 10 described above,
If in step S ₄ is determined that [Delta] T ₁ ≒ 0, although the degree of opening of the regulating valve 10 is maintained at the opening degree at that time in step S _6, the refrigerant by a bypass of the liquid refrigerant X ₂ to the refrigerant circulation line 2A When the dryness of the distribution system 2A is too small, it is determined that [Delta] T ₁ <0 in step S _4. At that time, the diaphragm by a predetermined amount the degree of opening of the control valve 10 in step S _7, reducing the bypass quantity of the liquid refrigerant X _2. In addition,
When the Note is determined that [Delta] T _1> 0 in step S _4, the opening degree of the regulating valve 10 in step S ₅ is further increased.

As described above, in the present embodiment, the opening degree of the control valve 10 is controlled so that the outlet refrigerant temperatures T ₁ and T ₂ of the refrigerant circulation systems 2A and 2B become substantially equal. In addition, refrigerant drift in the refrigerant distribution systems 2A and 2B is prevented, and the heat exchange performance in the refrigerant distribution systems 2A and 2B can be brought out to its full capacity. Incidentally, also in the case of the present embodiment, the liquid refrigerant X
₂ is bypassed to the outlet side of the dryness of greater refrigerant flow lines 2A by the energy held by the liquid refrigerant X ₂ because you have to utilize as a heat exchanger, it can be effectively utilized for the refrigerant.

Eighth Embodiment FIG. 16 shows the contents of the control means 21 in an air conditioner evaporator according to an eighth embodiment of the present invention.

In the case of the present embodiment, the signals from the thermistors 6 and 8 are to be input to the temperature difference calculating section 22 of the control means 21, and the detected temperatures T ₁ and T _{3 of the} thermistors 6 and 8 are input. Of the temperature difference ΔT ₂ = T ₁ −T ₃ . The other configuration is the same as that of the sixth embodiment, and the description is omitted to avoid duplication.

Next, the control of the opening of the control valve in the evaporator for an air conditioner of this embodiment will be described with reference to the flowchart shown in FIG.

[0064] are temporarily closed control valve 5 in Step S _1, the signal from the thermistor 6 and 8 in step S ₂ (i.e., the detected temperature T _1, T ₃₎ is inputted to the control means 21, the temperature in step S ₃ The difference ΔT ₂ = T ₁ −T ₃ is determined. Thereafter, the sign determination of the temperature difference [Delta] T ₂ in step S ₄ (i.e., the determination of [Delta] T _2> 0 or ΔT ₂ ≒ 0)
When it is determined that ΔT ₂ > 0, drift of the refrigerant occurs in the refrigerant distribution systems 2A and 2B (that is, the refrigerant flow in the refrigerant distribution system 2A is smaller than the gas refrigerant in the refrigerant distribution system 2B). since X ₁ and the ratio X ₁ / X ₂ between the liquid refrigerant X ₂ indicates a by being) that increases, by opening the control valve 10 by a predetermined angle in step S _5, the inlet pipe 1 of the liquid phase portion bypass of the liquid refrigerant X ₂ to the dryness is greater refrigerant flow line 2A takes place from 1b. Then, the refrigerant distribution system 2A
Dryness of decreases in the refrigerant circulation system 2A by a bypass of the liquid refrigerant X ₂ to the outlet refrigerant temperature T ₁ of the intermediate refrigerant temperature T ₃ of the refrigerant flow lines 2A are equal (i.e., the refrigerant flow line 2A, in 2B The control is performed in the direction in which the refrigerant is evenly distributed.

[0065] Thereafter, the control process returns to step S _2, the processing of steps S ₂ ~ Step S ₄ is performed,
As a result of equal distribution of the refrigerant by opening the control valve 10 described above,
If it is determined that [Delta] T ₂ ≒ 0 in step S _4, the opening degree of the regulating valve 10 is maintained to the opening degree at that time in step S _6, the change in the refrigeration cycle in step S ₇ (e.g., compressor frequency or fan rotation whether a change in such number) is is determined, in the case of affirmative determination is returned to step S _1, in the case of negative determination, the routine returns to step S _2. Incidentally, Note [Delta] T _2> 0 in step S ₄
If it is determined that the regulating valve 1 in step S ₅
The opening degree of 0 is further increased.

As described above, in the present embodiment, the outlet refrigerant temperature T ₁ and the intermediate-portion refrigerant temperature T ₃ in the refrigerant distribution system 2A where the degree of dryness is higher among the refrigerant distribution systems 2A and 2B.
And the opening degree of the control valve 10 is controlled so as to be substantially equal to each other. Therefore, refrigerant drift in the refrigerant distribution systems 2A and 2B is prevented, and the refrigerant distribution system 2
The heat exchange performance in A and 2B can be brought out to full capacity. In this embodiment, the inlet pipe 1
Since the liquid is bypassed to the outlet side of the large coolant flow line 2A of the dryness of the refrigerant X ₂ and has the energy held by the liquid refrigerant X ₂ so as to use as a heat exchanger, it can be effectively utilized for the refrigerant.

Ninth Embodiment FIGS. 18 and 19 show an air conditioner evaporator according to a ninth embodiment of the present invention.

In the case of the present embodiment, the downstream side of the control valve (hereinafter referred to as the second control valve) 10 in the liquid drain pipe 9 of the seventh embodiment and the liquid phase portion on the outlet side of the refrigerant flow system 2B having a small degree of dryness. A bypass control valve (hereinafter, referred to as a first control valve) 12 for controlling the flow rate of the liquid refrigerant is provided in the bypass pipe 11. Then, each of the refrigerant flow lines 2A, a thermistor 6 and 7 to act as a refrigerant temperature detecting means for detecting the outlet refrigerant temperatures T _1, T _2, respectively, in 2B, the refrigerant temperatures T ₁ detected by the respective thermistors 6,7 first control means 21 for controlling the opening degree of the first control valve 12 so that T ₂ is equal
A and the refrigerant temperatures T ₁ , T ₁ detected by the thermistors 6, 7 under the condition that the first control valve 12 is closed when the opening control by the first control means 21A becomes impossible. ₂ so that the second control valve 10 is equal to the second control valve 10.
And a second control means 21B for controlling the opening degree of the second control means.

The first control means 21A calculates a temperature difference ΔT ₁ = T ₁ −T ₂ between the outlet refrigerant temperatures T ₁ and T ₂ detected by the thermistors 6 and 7, as shown in FIG. A first temperature difference calculation unit 22A;
The first control valve based on the temperature difference [Delta] T ₁ determined by 1
And a first opening calculating section 23A for calculating the opening degree of the second opening degree, and a first opening degree calculating section 23A for obtaining the opening degree obtained by the first opening degree calculating section 23A.
First opening output section 24A that outputs an opening command to control valve 12
The second control means 21B calculates a temperature difference ΔT ₁ = T ₁ −T ₂ between the outlet refrigerant temperatures T ₁ and T ₂ detected by the thermistors 6 and 7. 22
B, a second opening calculator 23B for calculating the opening of the second control valve 12 based on the temperature difference ΔT ₁ obtained by the second temperature difference calculator 22B, and a second opening calculator 23B. And a second opening output section 24B for outputting an opening command to the second control valve 12 so as to obtain the opening determined by the above.

Next, the opening control of the control valve and the bypass control valve in this embodiment will be described with reference to the flowchart shown in FIG.

[0071] In step S ₁ is closed first and second control valves 12 and 10 once, the signal from the thermistor 6 at step S ₂ (i.e., the detected temperature T _1, T ₂₎
There is input to the first control means 21A, the temperature difference [Delta] T ₁ = T ₁ -T ₂ at step S ₃ is obtained. After a while
Code determination of the temperature difference [Delta] T ₁ in step S ₄ (i.e., delta
T ₁ > 0 or ΔT ₁ ≒ 0), and ΔT ₁
If it is determined that> 0, the refrigerant has drifted in the refrigerant distribution systems 2A and 2B (that is, the refrigerant distribution system 2A, 2B).
Since the A side side indicates the comparison ratio X ₁ / X ₂ between the gas refrigerant X ₁ and liquid refrigerant X ₂ becomes larger) that the refrigerant flow system 2B side, first adjustment in step S ₅ Valve 12
Is opened by a predetermined opening degree, and the refrigerant distribution system 2 having a small dryness
Bypass of the liquid refrigerant X ₂ to the dryness is greater refrigerant flow line 2A takes place from the liquid phase portion of the B. Then, along with the dryness of the refrigerant flow line 2B increases by a bypass of the liquid refrigerant X ₂ from the refrigerant circulation system 2B to the coolant circulation system 2A, the smaller the degree of dryness in the refrigerant circulation system 2A,
Control is performed in a direction in which the outlet refrigerant temperatures T ₁ , T ₂ of the refrigerant distribution systems 2A, 2B become equal (that is, the refrigerant is equally distributed in the refrigerant distribution systems 2A, 2B). Incidentally, when it is determined that [Delta] T ₁ ≒ 0 in step S _4, the opening degree of the first control valve 12 is maintained to the opening degree at that time in step S _6, the process returns to step S _2.

[0072] Not refrigerant flow lines 2A, the outlet refrigerant temperature difference [Delta] T ₁ ≒ 0 of 2B by opening degree control of the first control valve 12 in step S _5, there is a case where the first control valve 12 is fully opened since the first control valve 12 is in the fact that it is determined whether or not a fully opened in step S _7. If a negative determination is made here, step S ₂
Returns to, the processing of steps S ₂ ~ Step S ₄ is performed, the valve opening by the liquid refrigerant X of the first control valve 12 mentioned above
Results of _second bypass, if it is determined that [Delta] T ₁ ≒ 0 in step S _4, the opening degree of the regulating valve 10 in step S ₆ as described above is maintained at the opening degree at that time, on the other hand, in step S ₇ If an affirmative determination, the process proceeds to step S _8, closing the first control valve 12.

[0073] Thereafter, the signal from the thermistor 6 in step S ₉ (i.e., the detected temperature T _1, T ₂₎ is input to the second control means 21B, the temperature difference ΔT ₁ = T ₁ in step S ₁₀ - T ₂ is required. Thereafter, the sign determination of the temperature difference [Delta] T ₁ in step S ₁₁ (i.e., [Delta] T _1>
0, ΔT ₁ ≒ 0 or ΔT ₁ <0), and Δ
If it is determined that T ₁ > 0, the refrigerant circulation systems 2A, 2A
B has a drift in the refrigerant (that is, the refrigerant flow in the refrigerant flow system 2A is smaller than that in the refrigerant flow system 2B).
Since ₁ and the ratio X ₁ / X ₂ between the liquid refrigerant X ₂ indicates a by which) the larger, second regulating valve in step S ₁₂ 1
0 opened by a predetermined opening degree, the bypass of the liquid refrigerant X ₂ to the refrigerant circulation line 2A takes place from the inlet pipe 1 of the liquid phase portion 1b. Then, the dryness is reduced in the refrigerant circulation system 2A by a bypass of the liquid refrigerant X ₂ to the refrigerant circulation line 2A, the refrigerant flow line 2A, the outlet refrigerant temperature T ₁ of the 2B, T ₂ and are equal (i.e., refrigerant flow (Equal distribution of the refrigerant in the systems 2A and 2B is obtained).

[0074] Then, the change in the refrigerating cycle in step S ₁₅ (for example, changes such as the compressor frequency or fan speed) whether there has been is determined, the process returns to step S ₁ in the case of affirmative determination, negative determination returns to step S ₉ in the case of, step S ₉ ~ step S ₁₁
Of the processing is carried out, the results of the refrigerant even distribution according to the opening of the second control valve 10 mentioned above, [Delta] T ₁ in step S ₁₁
≒ 0 and it is determined, but the degree of opening of the second control valve 10 is maintained at the opening degree at that time in step S _13, the bypass of the liquid refrigerant X ₂ to the refrigerant circulation line 2A of the refrigerant flow lines 2A When the dryness is too small, it is determined that [Delta] T ₁ <0 in step S _11. In that case, step S
In ₁₄ squeeze the opening of the second control valve 10 by a predetermined amount, reducing the bypass quantity of the liquid refrigerant X _2. Incidentally, if it is determined in step S ₁₁ Note that [Delta] T _1> 0, the degree of opening of the second regulating valve 10 in step S ₁₂ is greater.

As described above, in this embodiment, the opening degree of the first control valve 12 is controlled so that the outlet refrigerant temperatures T ₁ and T ₂ of the refrigerant circulation systems 2A and 2B are substantially equal. Since the liquid refrigerant bypass to the refrigerant distribution system 2A is performed, and then the opening degree of the second control valve 10 is controlled, the liquid refrigerant bypass from the liquid phase portion 1b of the inlet pipe 1 to the refrigerant distribution system 2A is performed. Refrigerant distribution system 2A, 2
The refrigerant drift in B is more effectively prevented, and the heat exchange performance in the refrigerant distribution systems 2A and 2B can be drawn to its full capacity. Also in the case of the present embodiment, the liquid refrigerant X ₂ in the inlet pipe 1 is bypassed to the outlet side of the refrigerant distribution system 2A having a high degree of dryness, and the liquid refrigerant X ₂
Since the energy held by the heat exchanger is used for heat exchange, the refrigerant can be effectively used.

Tenth Embodiment FIG. 21 shows the contents of control means 21A and 21B in an air conditioner evaporator according to a tenth embodiment of the present invention.

In the case of this embodiment, the control means 21A, 21B
The signals from the thermistors 6 and 8 are to be input to the temperature difference calculation units 22A and 22B in the above, and the temperature difference ΔT ₂ = T ₁ −T ₂ between the detected temperatures T ₁ and T ₃ of the thermistors 6 and 8.
Has become the operation of T ₃ is made. The other configuration is the same as that of the ninth embodiment, and the description is omitted to avoid duplication.

Next, the control of the opening of the first and second control valves in the evaporator for an air conditioner of this embodiment will be described with reference to the flowchart shown in FIG.

[0079] In step S ₁ is closed first and second control valves 12 and 10 once, the signal from the thermistor 6 and 8 in step S ₂ (i.e., the detected temperature T _1, T ₃₎
There is inputted to the control unit 21A, the temperature difference ΔT ₂ = T ₁ -T ₃ is determined in step S _3. Thereafter, the sign determination of the temperature difference [Delta] T ₂ in step S ₄ (i.e., [Delta] T _2>
0 or ΔT ₂ ≒ 0), and when ΔT ₂ > 0 is determined, refrigerant drift has occurred in the refrigerant distribution systems 2A and 2B (that is, the refrigerant distribution system 2A side has a refrigerant flow). Gas refrigerant X ₁ and liquid refrigerant X ₂ compared to the distribution system 2B side
Since the ratio X ₁ / X ₂ indicates a by being) that increases with, opened by a predetermined opening degree of the first control valve 12 in step S _5, the liquid phase portion of the small degree of dryness refrigerant flow line 2B bypass of the liquid refrigerant X ₂ to the dryness is greater refrigerant flow line 2A made from. Then, the degree of dryness in the refrigerant distribution system 2A decreases, and the outlet refrigerant temperature T ₁ and the intermediate refrigerant temperature T ₃ of the refrigerant distribution system 2A become equal (that is, equal distribution of the refrigerant in the refrigerant distribution systems 2A and 2B is obtained. )
Control in the direction is provided. Incidentally, when it is determined that [Delta] T ₁ ≒ 0 in step S _4, in step S ₆ the opening of the first control valve 12 is maintained to the opening degree at that time, then change to a refrigeration cycle in step S ₇ (e.g. ,
Whether a change in such compressor frequency or fan speed) is is determined, in the case of affirmative determination step S ₁
Returns to the case of negative determination, the routine returns to step S _9.

[0080] Not refrigerant flow lines 2A, the outlet refrigerant temperature difference [Delta] T ₁ ≒ 0 of 2B by opening degree control of the first control valve 12 in step S _5, there is a case where the first control valve 12 is fully opened since the first control valve 12 is in the fact that it is determined whether or not a fully opened in step S _8. If a negative determination is made here, step S ₂
Returns to, the processing of steps S ₂ ~ Step S ₄ is performed, the valve opening by the liquid refrigerant X of the first control valve 12 mentioned above
Results of _second bypass, if it is determined that [Delta] T ₁ ≒ 0 in step S _4, the opening degree of the regulating valve 10 in step S ₆ as described above is maintained at the opening degree at that time, on the other hand, in step S ₈ If an affirmative determination, the process proceeds to step S _9, closing the first control valve 12.

[0081] Then, the signal (i.e., the detected temperature T _1, T ₃₎ from the thermistor 6 and 8 in step S ₁₀ is input to the second control means 21B, the temperature difference [Delta] T ₂ = T ₁ in step S ₁₁ - T ₃ is required. Thereafter, the sign determination of the temperature difference [Delta] T ₂ in step S ₁₂ (i.e., [Delta] T _2>
0, ΔT ₂ ≒ 0 or ΔT ₂ <0), and Δ
When it is determined that T ₂ > 0, the refrigerant circulation systems 2A, 2A
B has a drift in the refrigerant (that is, the refrigerant flow in the refrigerant flow system 2A is smaller than that in the refrigerant flow system 2B).
Since ₁ and the ratio X ₁ / X ₂ between the liquid refrigerant X ₂ indicates a by which) the larger, second regulating valve in step S ₁₃ 1
0 opened by a predetermined opening degree, the bypass of the liquid refrigerant X ₂ to the refrigerant circulation line 2A takes place from the inlet pipe 1 of the liquid phase portion 1b. Then, the dryness is reduced in the refrigerant circulation system 2A by a bypass of the liquid refrigerant X ₂ to the refrigerant circulation line 2A, and the outlet refrigerant temperature T ₁ of the intermediate refrigerant temperature T ₃ of the refrigerant flow lines 2A becomes equal (i.e., the refrigerant Distribution system 2A, 2B
In which the refrigerant is evenly distributed at the same time).

[0082] Then, the change in the refrigerating cycle in step S ₁₅ (for example, changes such as the compressor frequency or fan speed) whether there has been is determined, the process returns to step S ₁ in the case of affirmative determination, negative determination returns to step S ₁₀ in the case of, step S ₁₀ ~ step S
Although the process of ₁₂ is performed, the valve opening results in the refrigerant even distribution according to the second control valve 10 mentioned above, [Delta] T in step S ₁₂
If it is determined that ₂ ≒ 0, the degree of opening of the second control valve 10 is maintained at the opening degree at that time in step S _14. Incidentally, if it is determined in step S ₁₂ Note that [Delta] T _1> 0, the degree of opening of the second regulating valve 10 in step S ₁₃ is greater.

As described above, in this embodiment, the opening degree of the first control valve 12 is controlled so that the outlet refrigerant temperature T ₁ of the refrigerant distribution system 2A and the intermediate refrigerant temperature T ₃ are substantially equal. The liquid refrigerant is bypassed from 2B to the refrigerant distribution system 2A, and then the liquid refrigerant is bypassed from the liquid phase portion 1b of the inlet pipe 1 to the refrigerant distribution system 2A by controlling the opening of the second control valve 10. Therefore, refrigerant drift in the refrigerant distribution systems 2A and 2B is more effectively prevented, and the heat exchange performance in the refrigerant distribution systems 2A and 2B can be drawn to its full capacity. In the case of this embodiment also, the liquid refrigerant X ₂ of the inlet pipe 1 is bypassed to the outlet side of the dryness of greater refrigerant flow line 2A by utilizing the energy held by the liquid refrigerant X ₂ as heat exchanger As a result, the refrigerant can be effectively used.

The present invention is not limited to the configuration of each of the above-described embodiments, and it is a matter of course that the design can be changed as appropriate without departing from the gist of the invention.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of an evaporator for an air conditioner according to a first embodiment of the present invention.

FIG. 2 is an enlarged view of a portion A in FIG.

FIG. 3 is a schematic configuration diagram of an evaporator for an air conditioner according to a second embodiment of the present invention.

FIG. 4 is a block diagram showing the contents of control means in the air conditioner evaporator according to the second embodiment of the present invention.

FIG. 5 is a flowchart illustrating opening control of a control valve in the air conditioner evaporator according to the second embodiment of the present invention.

FIG. 6 is a block diagram showing the contents of control means in an evaporator for an air conditioner according to Embodiment 3 of the present invention.

FIG. 7 is a flowchart illustrating opening control of a control valve in an air conditioner evaporator according to a third embodiment of the present invention;

FIG. 8 is a schematic configuration diagram of an evaporator for an air conditioner according to a fourth embodiment of the present invention.

FIG. 9 is a schematic configuration diagram of an evaporator for an air conditioner according to a fifth embodiment of the present invention.

FIG. 10 is a flowchart illustrating opening degree control of a control valve in an air conditioner evaporator according to a fifth embodiment of the present invention.

FIG. 11 is a schematic configuration diagram of an evaporator for an air conditioner according to a sixth embodiment of the present invention.

FIG. 12 is an enlarged view of a portion A in FIG. 11;

FIG. 13 is a schematic configuration diagram of an evaporator for an air conditioner according to a seventh embodiment of the present invention.

FIG. 14 is a block diagram showing the contents of control means in an air conditioner evaporator according to a seventh embodiment of the present invention.

FIG. 15 is a flowchart illustrating opening degree control of a control valve in the evaporator for an air conditioner according to the seventh embodiment of the present invention.

FIG. 16 is a block diagram showing the contents of control means in the evaporator for an air conditioner according to the eighth embodiment of the present invention.

FIG. 17 is a flowchart illustrating opening control of a control valve in the evaporator for an air conditioner according to the eighth embodiment of the present invention.

FIG. 18 is a schematic configuration diagram of an evaporator for an air conditioner according to a ninth embodiment of the present invention.

FIG. 19 is a block diagram showing the contents of control means in an air conditioner evaporator according to a ninth embodiment of the present invention.

FIG. 20 is a flowchart illustrating opening degree control of a control valve in an air conditioner evaporator according to a ninth embodiment of the present invention.

FIG. 21 is a block diagram showing the contents of control means in an air conditioner evaporator according to embodiment 10 of the present invention.

FIG. 22 is a flowchart illustrating control of the opening of a control valve in an air conditioner evaporator according to a tenth embodiment of the present invention.

[Explanation of symbols]

1 is an inlet pipe, 1a is a gas phase, 1b is a liquid phase, 2A, 2
B is a refrigerant distribution system, 3 is an outlet pipe, 4 is a degassing pipe, 5
Is a control valve, 6, 7, and 8 are refrigerant temperature detecting means (thermistors), 9 is a drain pipe, 10 is a control valve (second control valve), 1
1 is a bypass pipe, 12 is a bypass control valve (first control valve), 21 is control means, 21A is first control means, 21
B is a second control means.

Continuation of front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F25B 39/02 F25B 41/00

Claims (9)

(57) [Claims] 1. A plurality of refrigerant distribution systems (2A), (2B)
An air conditioner evaporator configured to allow a refrigerant to be diverted to a refrigerant outlet (3) of the evaporator via a degassing pipe (4). Characteristic evaporator for air conditioners. 2. An outlet of the degassing pipe (4) is connected to an outlet side of the refrigerant flow system (2B) having a low dryness among the refrigerant flow systems (2A) and (2B). The evaporator for an air conditioner according to claim 1. 3. The gas vent pipe (4) is provided with a control valve (5) for adjusting the flow rate of the refrigerant gas, and controls the outlet refrigerant temperature in each of the refrigerant distribution systems (2A) and (2B). Refrigerant temperature detecting means (6), (7) for detecting each
And control means (21) for controlling the degree of opening of the control valve (5) so that the refrigerant temperatures detected by the respective refrigerant temperature detecting means (6) and (7) become equal. The evaporator for an air conditioner according to any one of claims 1 and 2, wherein 4. The gas vent pipe (4) is provided with a control valve (5) for adjusting the flow rate of the refrigerant gas, and has a high degree of dryness among the refrigerant distribution systems (2A) and (2B). Refrigerant temperature detecting means (6) for detecting an outlet refrigerant temperature and an intermediate refrigerant temperature in the refrigerant distribution system (2A),
(8) and control means (21) for controlling the opening of the control valve (5) so that the refrigerant temperatures detected by the refrigerant temperature detection means (6) and (8) become equal. The evaporator for an air conditioner according to claim 1, wherein the evaporator is an air conditioner. 5. A plurality of refrigerant distribution systems (2A), (2B)
An evaporator for an air conditioner configured to allow a refrigerant to flow to the refrigerant circulation system (2A) or (2B) through a liquid drain pipe (9). An evaporator for an air conditioner, wherein the evaporator is bypassed to an outlet side of a refrigerant circulation system (2A) having a large degree. 6. A control valve (10) for adjusting a flow rate of a liquid refrigerant is provided in the liquid drain pipe (9), and an outlet refrigerant temperature in each of the refrigerant distribution systems (2A) and (2B) is controlled. Refrigerant temperature detecting means (6), (7) for detecting each
And control means (21) for controlling the opening of the control valve (10) so that the refrigerant temperatures detected by the refrigerant temperature detection means (6) and (7) become equal. The evaporator for an air conditioner according to claim 5, wherein 7. A control valve (10) for adjusting a flow rate of a liquid refrigerant is interposed in the liquid drain pipe (9), and the refrigerant circulation systems (2A) and (2B) have a high degree of dryness. Refrigerant temperature detecting means (6) for detecting an outlet refrigerant temperature and an intermediate refrigerant temperature in the refrigerant distribution system (2A),
(8) and the control valve (1) so that the refrigerant temperatures detected by the refrigerant temperature detecting means (6) and (8) are equal.
The evaporator for an air conditioner according to claim 5, further comprising control means (21) for controlling the opening degree of (0). 8. A control valve (1) in said drain pipe (9).
A bypass pipe (11) for connecting the downstream side of the refrigerant flow system (0) and the liquid phase portion on the outlet side of the refrigerant flow system (2B) having a low dryness is provided, and the flow rate of the liquid refrigerant is adjusted in the bypass pipe (11). Refrigerant temperature detecting means (6), (7) for detecting an outlet refrigerant temperature in each of the refrigerant distribution systems (2A), (2B), while providing a bypass control valve (12) for performing the operation.
And a first control means (21A) for controlling the opening degree of the bypass control valve (12) so that the refrigerant temperatures detected by the refrigerant temperature detection means (6) and (7) become equal.
When the opening control by the first control means (21A) becomes impossible, the refrigerant temperature detection means (6),
Second control means (2) for controlling the opening of the control valve (10) so that the refrigerant temperatures detected by (7) become equal.
The evaporator for an air conditioner according to claim 5, wherein 1B) is additionally provided. 9. A control valve (1) in the drain pipe (9).
A bypass pipe (11) for connecting the downstream side of the refrigerant flow system (0) and the liquid phase portion on the outlet side of the refrigerant flow system (2B) having a low dryness is provided, and the flow rate of the liquid refrigerant is adjusted in the bypass pipe (11). And a refrigerant for detecting an outlet refrigerant temperature and an intermediate refrigerant temperature in the refrigerant distribution system (2A) having a large degree of dryness among the refrigerant distribution systems (2A) and (2B). Temperature detection means (6),
(8) first control means (21) for controlling the opening degree of the bypass control valve (12) so that the refrigerant temperatures detected by the refrigerant temperature detection means (6) and (8) become equal.
A) and when the opening control by the first control means (21A) becomes impossible, the bypass control valve (1
A second control for controlling the opening of the control valve (10) so that the refrigerant temperatures detected by the respective refrigerant temperature detecting means (6) and (8) are equalized in a state where 2) is closed. The evaporator for an air conditioner according to claim 5, further comprising means (21B).