JPS59117580A - Refrigerant composition - Google Patents

Abstract

PURPOSE:To provide the titled composition consisting of a non-azeotropic mixture of a refrigerant having lower boiling point than flon 22 and a refrigerant having higher boiling point than flon 22 at a ratio within a specific range, and capable of improving the efficiency of a heat pump keeping the refrigeration capacity without modification of the heat pump. CONSTITUTION:The objective composition is composed of a non-azeotropic mixture of (A) a refrigerant having lower boiling point than flon 22 (hereinafter called as R22) (preferably R503, R23, R13, R13B1, R125, etc.) and (B) a refrigerant having higher boiling point than R22 (preferably R500, R12, R152a, R124, etc.). The boiling point difference between the refrigerants is preferbly 20-60 deg.C. The boiling point of the saturated liquid of the composition is higher than that of R22, and the condensation point of the saturated vapor is lower than R22 under arbitrary pressure, or the boiling pressure of the saturated liquid of the composition is higher than that of R22 and the condensation pressure of the saturated vapor is lower than R22 an at arbitrary temperature. USE:Suitable for the heat pump for heating or cooling a room at about -20-+ 60 deg.C.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a refrigerant composition suitable for heat pump devices, particularly for heating and cooling.

(Configuration of conventional example and its problems) Conventionally, as a refrigerant for a heat pump device for heating and cooling purposes, within the heat source temperature range of -20°C to 60°C, Freon 22
(Dichlorofluoromethane, boiling point -40.8℃, R22
Freon-based refrigerants (hereinafter abbreviated as R-) have been widely used. However, the efficiency of heat pump equipment is naturally limited by the thermodynamic properties of the refrigerant, which is determined by the heat source temperature.In order to achieve energy savings, the higher the boiling point of the refrigerant, the greater the latent heat of vaporization. Because of its high efficiency, refrigerants with higher boiling points than R22 (e.g. R12
, R114, etc.). However, since a refrigerant with a higher boiling point than R22 has a large suction specific volume of the compressor, with the same compressor, the amount of refrigerant circulated during the refrigeration cycle is reduced, and the refrigeration capacity is also significantly reduced. On the other hand, in order to achieve the same capacity as R22 without aiming for high efficiency, it is necessary to increase the heat transfer area of the compressor and heat exchanger, which conflicts with the request to keep the size of the equipment moderate. It was something.

(Objective of the Invention) The object of the present invention is to provide a heat pump device that conventionally uses R22, while achieving higher efficiency than R22, while requiring major modification of the compressor, heat transfer area, etc. of the current heat pump device. The aim is to provide a new refrigerant composition free from the above, and to achieve this by using a mixed refrigerant of two or more components.

(Structure of the Invention) The refrigerant composition of the present invention comprises a refrigerant with a boiling point lower than R22 and a refrigerant with a boiling point lower than R22.
This can be achieved in an appropriate composition range in a non-azeotropic mixed refrigerant consisting of a combination of refrigerants having a boiling point higher than 22. A particularly desirable composition range is defined as R
It is preferable that the composition of the refrigerant having a lower boiling point than No. 22 is greater than the composition where the boiling point line intersects with the R22 boiling point and smaller than the composition where the dew point line intersects with the R22 boiling point.

The boiling point line in the T-X diagram represents the relationship between the composition and temperature at which the saturated liquid of the mixed refrigerant begins to boil, and the dew point line represents the relationship between the composition and temperature at which the saturated gas of the mixed refrigerant begins to condense. It represents. In addition, it is preferable that the boiling point difference between the refrigerant with a lower boiling point than R22 and the refrigerant with a higher boiling point than R22 to be combined is about 60 deg at the maximum, and conversely, if the boiling point difference becomes 20 deg or less, the effect will be considerably reduced. In some cases, the mixed refrigerant forms an azeotropic composition, which is undesirable.

(Explanation of Examples) Hereinafter, the refrigerant composition of the present invention will be illustrated together with Examples.

Example 1 FIG. 1 shows a heat pump device to which the refrigerant composition of the present invention is applied. ■ is a compressor, 2 is a refrigerant-to-water double pipe condenser, 3
4 is a manual expansion valve, and 4 is a refrigerant-to-water double pipe evaporator.

In the first embodiment, R is a refrigerant with a lower boiling point than R22.
13B1 (boiling point -57.8°C), R12 (boiling point -29.8°C) is used as a refrigerant with a higher boiling point than R22, and R13
The molar fraction X of B] was made variable from O to 1. In addition, in the experiment, water was flowed in the condenser 2 and the evaporator 4 so that the refrigerant and water were in counterflow. The amount of water and the opening degree of the manual expansion valve 3 were adjusted to 10°C. Comparing these results with the case where R22 is applied using the same heat pump equipment, the performance coefficient (-evaporator 4 refrigeration capacity/compressor 1 manual power) and refrigeration capacity are related as shown in Figure 2. was gotten. That is, X20~0.5
Although the refrigerating capacity was slightly lower than that of R22 in the range of , the coefficient of performance was improved compared to R22, and at X20.2, an improvement of about 20% in the coefficient of performance was observed. This is thought to be due to the fact that losses in the heat exchange process were reduced by making the refrigerant and water flow in opposite directions.

In addition, in the R13B1/R12 mixed refrigerant, R], 3B
The vapor pressure of the saturated solution was measured while changing the composition of No. 1 as appropriate, and the T-X diagram at atmospheric pressure was estimated using these data, which is shown in FIG. In Figure 3, R22
When the boiling point (-40.8°C) is entered, the relationship between the improvement in the coefficient of performance seen in FIG. 2 and the composition of R13B1 in the mixed refrigerant becomes clearer. In other words, the range from the composition where the R22 boiling point and the boiling point line intersect (X2O,OS) to the composition where the R22 boiling point and the dew point line intersect (X = 0.44) is the range in which the coefficient of performance improves over R22 in Figure 2. included in. Also, in the range of X20, 08 to 0.44, (6
) The refrigerating capacity is 078 to 1.01 times that of R22, and both the coefficient of performance and the refrigerating capacity are improved compared to R12 alone (x=00). Therefore, in order to improve efficiency instead of R22, R12
R13B]/R12 mixed refrigerant is more desirable than R13B]/R12 mixed refrigerant.
It is considered that there is no need to significantly modify the heat pump device in order to obtain the same capacity as No. 22.

Example 2 The second example, like the first example, was carried out using the heat pump apparatus shown in FIG. 1 using the same experimental method. The mixed refrigerant used here was R502 (azeotropic refrigerant of R22 and R115, boiling point -
45.6℃), R is a refrigerant with a higher boiling point than R22]
14 (boiling point 3.8°C). When the results at this time were compared with the case of R22, the same relationship as shown in FIG. 4 was obtained. In this case, the coefficient of performance is better than R22 in almost all composition ranges, especially in X20.2
Although an improvement of about 30% is seen in ~0 and 3,
Refrigeration capacity has significantly decreased to less than 40%.

Also, the same as in the first embodiment (the estimated T-X diagram is shown in Figure 5, but the R22 boiling point (-40
, 8°C), it is possible to specify the heavy composition range of the mixed refrigerant that should replace R22. That is, R2
From the composition where 2 and the boiling point line intersect (x = 0.79), R22
In the composition range (X20.97) where the dew point line intersects, the coefficient of performance is 1.17 to 100 times that of R22, and the refrigerating capacity is 0.72 to 0.93 times that of R22. Therefore, although it cannot be said that maximum efficiency is achieved in this composition range, the coefficient of performance can be improved without major modification of the heat pump device.

As can be seen from the above examples, the medium composition of the present invention is
It is a non-azeotropic mixed refrigerant consisting of a combination of a refrigerant with a lower boiling point than R22 and a refrigerant with a higher boiling point than R22, and its heavy composition range can be roughly specified as follows. The first method, as shown in Figure 6, is to specify a composition range in which the boiling temperature of the saturated liquid at a given pressure of the mixed refrigerant is lower than R22, and the condensation temperature of the saturated gas is higher than R22. . Note that it is convenient to use atmospheric pressure as the arbitrary pressure. As a second specific method, as shown in FIG. 7, the composition range can be specified such that the boiling pressure of the saturated liquid is higher than R22 and the condensation pressure of the saturated gas is lower than R22 at any temperature. Note that there is no significant difference in the range whether the first or second method for specifying the composition range is used.

Next, as a combination of mixed refrigerants, the boiling point difference is 20 to 5 Q
A refrigerant with a boiling point lower than R22 is preferably R503, R23, R13°R13B1.
R32,R], 25. Examples of refrigerants with higher boiling points than R22, such as R502, are R500, R12°R152a, R12
4JR142b, R12B1.

Examples include R114, R133a, R21, and R11.

In addition, in the combination of a refrigerant with a boiling point lower than R22 and a refrigerant with a higher boiling point than R22, the composition range based on the low boiling point refrigerant is such that the lower the boiling point of the low boiling point refrigerant, the less the low boiling point refrigerant. (9), and the higher the boiling point of the high boiling point refrigerant, the more the low boiling point refrigerant.

(Effect of the invention) The mixed refrigerant and its composition range specified in the present invention do not have the same boiling point and dew point like a single refrigerant, but the average value is almost the same boiling point as R22. The compressor suction specific volume is also almost the same as R2'2, making it possible to improve efficiency while maintaining refrigeration capacity without major modification of the heat pump device. It is particularly suitable for heat pump devices for air conditioning and heating in which the heat source temperature range is about 120°C to 60°C.

[Brief explanation of the drawing]

Fig. 1 shows an example of a heat pump device to which the refrigerant composition of the present invention is applied, and Figs. 2 and 4 show the relationship between the mixed refrigerant composition, coefficient of performance, and refrigerating capacity compared to R22. Figures 3 and 5 are diagrams showing the relationship between the mixed refrigerant composition and temperature at atmospheric pressure, and Figures 6 and 7 are diagrams showing the method for specifying the composition range of the refrigerant composition of the present invention. FIG. (10) 1... Compressor, 2... Condenser, 3... Manual expansion valve, 4... Evaporator. (11) Figure 1 Figure 2 Wandering of R13B1 in R13B1/R12+ 1 Figure 3 Wandering of R13B'l in R13B1/R12 4th
Figure R502/R114 templeill R502*(A/IP'
f-Fig. 5 Fig. 6 t4': 11 ya r)

Claims (3)

[Claims] (1) In a non-azeotropic mixed refrigerant consisting of two or more components, which is a combination of a refrigerant with a lower boiling point than R22 and a refrigerant with a higher boiling point than R22, A. The boiling temperature of the saturated liquid at any pressure is lower than that of R22. , and the condensation temperature of the saturated gas is higher than R22, or B. The boiling pressure of the saturated liquid at any temperature is higher than R22, and the condensation pressure of the saturated gas is lower than R22. 1. A refrigerant composition characterized in that it has a composition range and is used in a heat pump device for heating and cooling. (2) R503°R23 as a refrigerant with a lower boiling point than R22
, R13, R13B1, R125, R502, and has a higher boiling point than R22, such as R500, R12°RI52a, RJ24,
R142b, R12B1. The refrigerant composition according to claim (1), which contains at least one of R114, R133a, R21, and R11. (3) The refrigerant composition according to claim (1), characterized in that it consists of two components with a boiling point difference of 20 to 60 degrees.