JPS5862469A - Heat pump type refrigerator - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a heat pump type refrigeration system using a non-azeotropic mixed refrigerant as a refrigerant.

A heat pump type cooling outlet using a non-azeotropic mixed refrigerant exhibits a lower temperature, and the temperature difference between the inlet and outlet is larger than that in a cycle using a single refrigerant.

Figures 1 and 2 show this relationship on a temperature (T)-entropy (8) diagram. Figure 1 is for a non-azeotropic mixed refrigerant, and Figure 2 is for a single refrigerant. This is the refrigeration cycle in case. In the figure, 1a and Ib are the suction state of the compressor, 2a and 2b
is the state after being compressed by the compressor, 2m, 2b 8a
, 8b, 4a, and 4b are all under equal high pressure. In the condenser, it is cooled from the states 2a and 2b to reach the dew point states 11i8a and 8b, and then the boiling point states 4a and 4b.
cooled down to As is clear from FIG. 2, in a single refrigerant cycle, a state change occurs at the same temperature under the same pressure conditions from the dew point of 8b to the boiling point of 4b. On the other hand, in a cycle using a non-azeotropic mixed refrigerant consisting of a high boiling point refrigerant and a low boiling point refrigerant, under the same pressure conditions from the dew point of 8a to the boiling point of 4a, the temperature is not constant and the dew point is 8a.
The temperature is high in the vicinity of , mainly because high boiling points condense.
Near the boiling point 4a at the condenser outlet, the temperature is low because low boiling point components are mainly condensed.

Further, in Fig. 2, 5a and 5b indicate the low pressure 4&a after being expanded by the throttle, and 5a, 5b, Ia, and 1b are all in the same low pressure state.

In the evaporator, it is heated from the states 5a and 5b to the states Ia and Ib. In a single refrigerant cycle, a state change occurs at the same temperature under the same pressure conditions from 5b to 1b. On the other hand, in a non-azeotropic mixed refrigerant cycle, 5a to 1
Under the same pressure conditions up to 8, the temperature is not constant; near the evaporator inlet 58, the temperature is low because mainly low-boiling components evaporate, and near the evaporator outlet 1b, mainly high-boiling components evaporate. Therefore, the temperature is high. As described above, a temperature difference between the inlet and the outlet of the evaporator occurs in a non-azeotropic mixed refrigerant cycle, which is greater than that which occurs in a single refrigerant cycle.

Figures 3 and 4 are configuration diagrams of conventional ones, respectively.
101 is a compressor, 102 is a four-way switching valve, 108 is a fin-and-tube type outdoor air heat exchanger, 104 is an outdoor blower, 1o5 is a gear pilar tube (capillary tube), +
06 is fin and tube type indoor air heat exchange H)
3° 107 indicates an indoor blower, during cooling, the refrigerant circulates as shown by the dashed arrow, and during heating, the flow is reversed by the four-way switching valve 102, and the refrigerant circulates as shown by the one-point M-line arrow. In a refrigeration cycle constructed in this way, 1, for example, R-18
Non-common n1 obtained by mixing two types of refrigerants with different boiling points, B+ and R-1528, at a ratio of 70% and 30%, respectively.
;Encloses mixed refrigerant. The indoor heat exchanger 106 functions as an evaporator during cooling and as a condenser during heating;
The outdoor heat exchanger +08 works as a condenser during cooling and as an evaporator during heating. Since these refrigeration effects have already been described in FIGS. 1 and 2, their explanation will be omitted.

Now, focusing on the outdoor heat exchanger 103 shown in FIG. 8, when it acts as a condenser during cooling, the inlet section 108a of the refrigerant tube is arranged upwind with respect to the outlet section +08b.

The outlet portion 103b is arranged to be downwind with respect to the inlet portion 108a. In the figure, solid arrows indicate the flow direction of air driven by the blower, 10i11c indicates a tube through which the refrigerant passes in the heat exchanger, and 1011d indicates a large number of fins arranged in the heat exchanger.

In the operating state of a refrigeration cycle using such a non-azeotropic mixed refrigerant, the heat exchanger 108 operates as a condenser during cooling.
As mentioned above, the inlet section 108a of the refrigerant tube exhibits a high temperature due to its characteristics, and the outlet section +08b has a low temperature, but heat exchange at the outlet section 108b is impaired due to the hot air generated from the inlet section 108a. Re.

In order to solve the above-mentioned drawback, it is difficult to achieve good condensation, as shown in FIG.

It is conceivable to arrange the refrigerant tube inlet portion 108a of the heat exchanger 108, which operates as a condenser, to be downwind with respect to the outlet portion 108b, and to be upwind with respect to the outlet portion 103a. In this case, since the outlet portion 108b is located upwind, the inlet portion 108b
It is not affected by the hot air generated from a, but on the contrary, its inlet part 1
In order to cool down 0i11a and bring it to a low temperature as a whole,
Efficient condensation can be performed.

However, in the heat pump type refrigeration system, it is possible to switch to the heating cycle using the four-way switching valve 1o. The direction of flow is reversed. As a result, as in the example shown in FIG. 4, the refrigerant tube inlet portion 1011b is placed upwind of the outlet portion 108a, and the outlet portion 108m is placed downwind of the inlet portion +08b. Due to the characteristics of the non-azeotropic mixed refrigerant, the inlet section 1011b of the evaporator is at a low temperature, and the outlet section 108a is at a low temperature.
Since the temperature becomes high, the air blower 104 is used to forcefully ventilate the air.

The high temperature portion 103a corresponding to the exit portion is due to the cold air from the low l crystal portion 108b placed upwind.

The temperature difference between the air and the refrigerant will decrease and the boiling of the refrigerant will be impaired.

As mentioned above, the refrigerant tubing in the heat exchanger is arranged in one part and the outlet part when a non-azeotropic mixed refrigerant is used. However, in a heat pump type refrigeration system, the four-way switching valve reverses the flow of the refrigerant, so even if you select counterflow during cooling, parallel flow occurs during heating, that is, the outlet section is placed downwind. This has the disadvantage that efficient heat exchange is impaired because the inlet part is placed in the wind (and vice versa).

The present invention has been proposed in view of the above points, and its purpose is to provide an efficient heat pump type refrigeration system.

The present invention provides a heat pump type refrigeration system using a non-azeotropic mixed refrigerant consisting of a low-boiling point refrigerant and a high-boiling point refrigerant. It is characterized by being placed parallel to the flow, and may also act as a condenser.

Even when acting as an evaporator, the thermal influence of the inlet section of the refrigerant tube does not affect the outlet section, so that efficient heat exchange is performed in either case. Therefore, an efficient heat pump type refrigeration system can be obtained.

The present invention will be explained below based on two examples.

In FIG. 5, 201 is a compressor, 202 is a four-way switching valve, 208 is a fin-and-tube type outdoor heat exchanger,
204 is an outdoor fan.

205 is a gear pillar tube, 206 is a fin-and-tube type indoor heat exchanger, and 207 is an indoor blower.

These devices are connected in the order shown in the figure, and the refrigeration cycle configured in this way contains two types of refrigerants, for example, R-18111 and R-152a, each having a different boiling point.
%, a non-azeotropic mixed refrigerant mixed at a ratio of 80% is enclosed. When the refrigerant tube of the outdoor heat exchanger 208, which operates as a condenser during cooling operation, is divided into two approximately at the center, the inlet portion 208a and the outlet portion 208b are arranged in parallel with the flow of air. There is.

Note that the indoor heat exchanger 206 also has a similar configuration.

During cooling operation, when the compressor 201 is started, R-18DI
The non-azeotropic mixed refrigerant consisting of
1, and as shown by the dashed arrow, the four-way switching valve 2
02, an outdoor heat exchanger 20 that operates as a condenser.
8, where it is condensed and liquefied, passed through a capillary pipe 205, and evaporated in an indoor heat exchanger 206 to provide a cooling effect. The evaporated and vaporized non-azeotropic mixed refrigerant is sucked into the compressor 201 via the four-way switching valve 202 . Due to the characteristics of non-azeotropic mixed refrigerants, under the same pressure conditions, the inlet section between the center and the inlet of the condenser exhibits a high temperature, and the outlet section between the center and the outlet exhibits a low temperature. This is as stated above.

As described above, the refrigerant tube inlet portion 203a and the outlet portion 208b are placed in parallel so that they both face upwind against the forced ventilation by the blower 204, so the hot air generated at the inlet portion is Without affecting the outlet section, efficient heat exchange is performed in both the inlet section and the outlet section as a whole, and efficient condensation can be performed.

On the other hand, during heating operation, the flow of the refrigerant is reversed by the four-way switching valve 202, and the outdoor heat exchanger 208 functions as an evaporator, with the refrigerant tube inlet portion corresponding to 208b and the outlet portion corresponding to 203a.

In this case as well, due to the characteristics of the non-azeotropic mixed refrigerant, the inlet portion 208b
is at a low temperature, and the outlet section 203a is at a high temperature, but the inlet section 2
08b and the outlet section 208a are placed in parallel so as to face upwind, so the cold air generated at the inlet section does not affect the outlet section, and both the inlet and outlet sections are heated efficiently. Exchange is performed, and efficient evaporation can be performed.

In addition, the above-mentioned R-18B1 and R are used as non-azeotropic mixed refrigerants.
- Not limited to combination with 162a.

Further, the mixing ratio is not limited to the above-mentioned values of 70% and 80%.

As mentioned above, considering the operation of the condenser and evaporator as heat exchangers for heat pump refrigeration equipment, some or all of the inlet and outlet portions of the refrigerant tubes should face upwind, and the Since it is placed in parallel with the flow of air, the thermal influence at the inlet (i.e., high temperature hot air during condensation and low temperature cold air during evaporation) does not affect the outlet section.

Efficient heat exchange can be performed during both condensation and evaporation, resulting in improved performance.

FIG. 6 shows an embodiment in which the number of circuits in the heat exchanger is plural. In this case, for each circuit, the inlet portion 308a and the outlet portion 303b are arranged in parallel with the wind flow, so that the same effect as described above is produced.

The single broken line arrow in Figure 1 indicates the flow of refrigerant during cooling.

The one-dot chain arrow indicates the flow of refrigerant during heating, 803 indicates an outdoor heat exchanger, and 307 indicates an outdoor blower 11105 indicates a capillary tube.

[Brief explanation of the drawing]

FIG. 1 is a temperature-entropy diagram of a refrigeration cycle using a single refrigerant, and FIG. 2 is a temperature-entropy diagram of a refrigeration cycle using a non-azeotropic mixed refrigerant. 8 and 4 are block diagrams showing different conventional examples, FIG. 5 is a block diagram showing one embodiment of the present invention, and FIG. 6 is a block diagram of main parts showing another embodiment. . 201; Compressor, 202i four-way switching valve. 20!1,1108i outdoor heat exchanger, 208a. 110111a; entrance part, 208b, 1108bt
Outlet part, 208c; Refrigerant tube, 208di fin, 204. Outdoor blower, 205.805, capillary tube, 206. Indoor heat exchanger, 207,807.
Indoor blower. 1 Tropi (S) Hawk 1 Flash 1 Tropi ° (S) Chi 2 Crop

Claims (1)

[Claims] In a heat pump type refrigeration system that uses a non-azeotropic mixed refrigerant consisting of a low-boiling point refrigerant and a high-boiling point refrigerant, when the refrigerant tube of an indoor or outdoor heat exchanger is divided into two approximately at the center, the 9-way section will be separated from the wind flow. A heat pump type refrigeration device characterized by being arranged in parallel.