JPH07174420A - Freezing device - Google Patents

Abstract

PURPOSE:To change the composition of a refrigerant circulating through a freezing cycle and to improve efficiency by a method wherein when the amount of a refrigerant dissolved in lubricating oil is varied with the change of the temperature and the pressure of lubricating oil. CONSTITUTION:High-temperature high-pressure refrigerant steam compressed by a compressor 1 releases heat in a condenser 2 and condensed and liquefied. Thereafter, the refrigerant steam is reduced in pressure and expanded by a throttling device 3 and produces a gas-liquid two-phase refrigerant. The refrigerant absorbs heat in a vaporizer 4 for vaporization and gasification and turns into refrigerant steam and is sucked in the compressor 1 again. In this case, lubricating oil during a freezing cycle having characteristics differing with the change of temperature and pressure from those of the refrigerant is used. In this case, the temperature of lubricating oil in the compressor 1 is controlled by a lubricating oil temperature regulator 5. This constitution varies generation capacity by changing the composition of lubricating refrigerant and improves efficiency.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration system using a non-azeotropic mixed refrigerant.

[0002]

2. Description of the Related Art In recent years, a mixed refrigerant has been attracting attention as an alternative refrigerant for a refrigerating apparatus in accordance with the regulations of CFC and HCFC. A refrigeration system using a mixed refrigerant can perform capacity control and performance improvement by varying the composition ratio of the refrigerant circulating inside the cycle.

Conventionally, a rectification separation system utilizing a difference in boiling point has been used as a system for varying the composition of the refrigerant circulating in the cycle of a refrigerating apparatus using a non-azeotropic mixed refrigerant, for example (for example, Japanese Patent Laid-Open Publication No. 2000-242242). 61-101757).

An example of a refrigerating apparatus using a rectification separation system will be described below with reference to FIG.

FIG. 7 is a refrigeration cycle diagram showing a conventional example. In FIG. 7, 31 is a compressor, 32 is a condenser, and 33.
Is a main expansion device, and 34 is an evaporator connected in an annular shape to form a main circuit. On the other hand, the outlet of the condenser 32 and the rectification tower 36
Is connected to the inlet of the pipe 40 by a pipe 40, and the heater 35 is connected to the pipe 40 in a heat exchange manner. In addition, the lower outlet of the rectification column 36 and the inlet of the evaporator 34 of the main circuit are connected to the auxiliary expansion device 3
The pipes 41 and 42 are connected to each other via 7. Further, a cooler 38 and a reservoir 39 are provided above the rectification column 36, and the reservoir 39 is connected to the rectification column 3 by pipes 43 and 44.
It is connected to 6 in a ring shape. In addition, the cooler 38 and the pipe 4
3 and 3 are connected by heat exchange. Here, the heat source of the heater 35 and the cooler 38 uses the discharge gas and the suction gas of the compressor 31. As the refrigerant, a non-azeotropic mixed refrigerant composed of two kinds of refrigerants having different boiling points is used. The operation of the refrigerating apparatus configured as described above, in which the filling material 45 is filled in the rectification column 36, will be described below.

First, the case where rectification separation is not performed will be described. A part of the high-pressure liquid refrigerant discharged from the condenser 32 is the pipe 4
Branched by 0. At this time, if the valve opening of the sub expansion device 37 is increased, the flow rate of the branch refrigerant branched to the pipe 40 increases, and heating of the heater 35 becomes insufficient, so steam is not generated,
Liquid refrigerant flows in from the lower inlet of the rectification tower 36. As a result, the rectification action does not proceed, the liquid refrigerant rises inside the rectification tower 36, enters the reservoir 39 through the pipe 43, and the pipe 44
To return to the rectification tower 36 again. Then, the pressure is reduced by the sub expansion device 37 and merges with the main circuit side refrigerant.

In this way, the composition ratio of the low boiling point components inside the reservoir 39 does not rise, so that the composition ratio of the main circuit becomes equal to the refrigerant charging ratio.

Next, the case of performing rectification separation will be described. When the valve opening of the sub expansion device 37 is reduced from the above state, the flow rate of the branched refrigerant decreases, and the liquid refrigerant that has branched from the condenser 32 is heated by the heater 35 and partially vaporized. It flows in from the lower entrance of the distillation column 36. This gas component rises in the clearance of the packing material 45 in the rectification tower 36, enters the cooler 38 through the pipe 43 from the upper outlet, is cooled and liquefied, and enters the reservoir 39. A drop A is provided in advance between the reservoir 39 and the return pipe 44 of the rectification tower 36.
As a result, a part of the liquid refrigerant from the reservoir 39 is returned to the rectification tower 36 through the pipe 44, and the clearance of the packing material 45 is lowered.
It makes gas-liquid contact with vapor rising in the middle, and performs rectification by heat exchange and mass transfer. Refrigerant with many low boiling point components is stored in the reservoir 39, and the refrigerant from the bottom of the rectification tower 36 is low. The refrigerant having a small boiling point component is the pipe 41 and the auxiliary expansion device 3.
7. Flow into the main circuit through the pipe 42.

Therefore, the low boiling point component ratio of the main circuit decreases and the high boiling point component ratio increases. As described above, by controlling the valve opening of the auxiliary expansion device 37, the amount of steam generated is adjusted to perform rectification separation, and the composition ratio of the refrigerant stored in the reservoir 39 is changed, whereby the main circuit refrigerant is The composition ratio of can be made variable.

[0010]

However, the above structure has the following problems.

In order to perform rectification separation, it is necessary to perform heating and the like and to inject the refrigerant vapor from the lower part of the rectification tower. However, since a high-temperature discharge refrigerant is used for the heater, the temperature at the inlet of the condenser decreases during heating operation. Therefore, the heating capacity is reduced. Further, when the intake superheat is increased by controlling the compressor intake superheat, it is inevitable that the cooling amount by the cooler is decreased and the separation performance is deteriorated.

The present invention solves the above-mentioned problems of the prior art, and when the amount of the refrigerant dissolved in the lubricating oil increases or decreases as the temperature or pressure of the lubricating oil changes, the change characteristics of each refrigerant are used. The purpose of this is to improve the efficiency by changing the composition of the refrigerant circulating in the refrigeration cycle by using the lubricating oil having different characteristics.

[0013]

In order to solve the above-mentioned problems, a refrigeration system of the present invention comprises a compressor, a condenser, a throttle device, and an evaporator connected in a ring to form a refrigeration cycle, which is non-common as a refrigerant. When two or more types of boiling refrigerants are mixed and used, and when the amount of refrigerant dissolved in the lubricating oil increases or decreases with changes in the temperature and pressure of the lubricating oil, the change characteristics are Lubricating oils having different characteristics are used, and a lubricating oil temperature controller for controlling the temperature of the lubricating oil in the compressor is provided.

Another refrigerating apparatus of the present invention is a compressor,
A condenser, an expansion device, and an evaporator are connected in a ring to form a refrigeration cycle, and HFC32 / HFC125 / H is used as a refrigerant.
When FC134a is used and the amount of the refrigerant dissolved in the lubricating oil increases or decreases as the temperature or pressure of the lubricating oil changes,
A lubricating oil temperature regulator is used which controls the temperature of the lubricating oil in the compressor by using the lubricating oil whose changing characteristics have different characteristics for the respective refrigerants used.

Another refrigeration system of the present invention is a compressor,
A condenser, an expansion device, and an evaporator are annularly connected to form a refrigeration cycle, HFC32 / HFC134a is used as a refrigerant, and the amount of the refrigerant dissolved in the lubricating oil increases and decreases as the temperature and pressure of the lubricating oil change. In this case, a lubricating oil whose change characteristics have different characteristics for the respective refrigerants used is used, and a lubricating oil temperature controller for controlling the temperature of the lubricating oil in the compressor is further provided.

[0016]

The present invention has the following functions due to the above-mentioned structure.

That is, a compressor, a condenser, a throttle device, and an evaporator are connected in a ring to form a refrigeration cycle, and two or more non-azeotropic refrigerants are mixed and used as refrigerants. When the amount of dissolved refrigerant changes with changes in the temperature and pressure of the lubricating oil, use a lubricating oil whose change characteristics have different characteristics for each refrigerant used. It is possible to realize a refrigerating apparatus that includes a lubricating oil temperature controller that controls the temperature of [3] and that can control the capacity and improve the performance by actually changing the composition of the refrigerant circulating in the refrigeration cycle.

[0018]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a refrigerating cycle diagram in the first embodiment of the refrigerating apparatus of the present invention. In the figure, 1 is a compressor, 2 is a condenser, 3 is a throttle device, and 4 is an evaporator, each of which is connected in an annular shape to form a refrigeration cycle. 5 is a lubricating oil temperature controller.

FIGS. 2 (a) and 2 (b) are examples of diagrams showing the relationship between the rate of dissolution of each refrigerant in lubricating oil and the temperature and pressure.

In this refrigeration cycle, a heating operation using a high capacity refrigerant amount α and a low capacity refrigerant amount β of a non-azeotropic mixed refrigerant will be described. The high-temperature and high-pressure refrigerant vapor compressed by the compressor 1 radiates heat in the condenser 2 and is condensed and liquefied. Thereafter, the expansion device 3 decompresses and expands to become a gas-liquid two-phase refrigerant, which absorbs heat in the evaporator 4 and evaporates to vaporize to become a refrigerant vapor, which is again sucked into the compressor 1.

At this time, a part of the lubricating oil in the refrigeration cycle circulates in the refrigeration cycle together with the refrigerant, but most of it remains inside the compressor 1. At this time, the temperature of the lubricating oil inside the compressor 1 is controlled by the lubricating oil temperature regulator, and the pressure is determined by the operating conditions, and the pressures are as shown in FIGS.
In the P ₁ and T ₁ states, the corresponding amounts of the refrigerants are dissolved in the lubricating oil. Therefore, the amount of high-performance refrigerant in the refrigerant actually circulating in the refrigeration cycle is (α-α ₁ )
Becomes Similarly, the low capacity refrigerant amount is (β-β ₁ ).

Next, when the cooling operation is performed, the temperature and pressure inside the compressor 1 move to the states of P ₂ and T ₂ in FIGS. 2A and 2B, and the amount of refrigerant dissolved in the lubricating oil is also changed. The amount of high-performance refrigerant in the refrigerant that changes and actually circulates in the refrigeration cycle is (α-α
₂ ) and the low capacity refrigerant amount becomes (β-β ₂ ).

Α ₁ shown in FIGS. 2A and 2B,
As can be seen from α ₂ , β ₁ and β ₂ , the composition of the circulating refrigerant during heating operation is (α-α ₁ ) :( β
-Β ₁ ). On the other hand, the composition of the circulating refrigerant during the cooling operation is (α-α ₂ ) :( β-β ₂ ) for the high-performance refrigerant and the low-performance refrigerant, and the ratio of the high-performance refrigerant is higher during the heating operation. Generally, in the case of an air conditioner, the refrigerating capacity required in the heating operation is larger than the refrigerating capacity required in the cooling operation, but in the refrigerating apparatus of the present invention, the generating capacity can be changed by changing the composition of the circulating refrigerant. It is possible to improve efficiency.

Next, a second embodiment of the present invention will be described with reference to the drawings. FIG. 3 shows a second refrigeration system of the present invention.
It is a refrigerating cycle figure in the Example of.

In the figure, reference numeral 11 is a compressor, 12 is a condenser, 13 is a throttle device, and 14 is an annular ring connected to an evaporator to form a refrigeration cycle. Reference numeral 15 is a lubricating oil temperature controller.

FIGS. 4 (a) to 4 (c) are examples of diagrams showing the relationship between the rate of dissolution of the refrigerant in the lubricating oil and the temperature / pressure.

In this refrigeration cycle, the case of heating operation with the HFC32 amount α, the HFC125 amount β, and the HFC134a amount γ will be described first. The high-temperature and high-pressure refrigerant vapor compressed by the compressor 11 radiates heat in the condenser 12 and is condensed and liquefied. Then, the expansion device 13 decompresses and expands to become a gas-liquid two-phase refrigerant, which absorbs heat in the evaporator 14 and evaporates to vaporize to become a refrigerant vapor, which is again sucked into the compressor 11.

At this time, a part of the lubricating oil in the refrigeration cycle circulates in the refrigeration cycle together with the refrigerant, but most of it remains inside the compressor 11. At that time, the temperature of the lubricating oil inside the compressor 11 is controlled by the lubricating oil temperature controller,
The pressure is determined by the operating conditions and is shown in Fig. 4 (a)-
In the state of P ₁ and T _{1 in} (c), the corresponding amounts of the refrigerants are dissolved in the lubricating oil. Therefore, the amount of HFC32 in the refrigerant actually circulating in the refrigeration cycle is (α-
α ₁ ). Similarly, the amount of HFC125 is (β-β ₁ ), H
The FC134a amount is (γ-γ ₁ ).

Next, when the cooling operation is performed, the temperature and pressure inside the compressor 11 move to the states of P ₂ and T ₂ in FIGS. 4A to 4C, and the amount of the refrigerant dissolved in the lubricating oil is also changed. The amount of HFC32 in the refrigerant that has changed and actually circulated in the refrigeration cycle is (α-α
₂ ) Similarly, the amount of HFC125 is (β-β ₂ ), HF
The amount of C134a is (γ-γ ₂ ).

Α ₁ , α ₂ , shown in FIGS. 4A to 4C,
As can be seen from β ₁ , β ₂ , γ ₁ , and γ ₂ , the composition of the circulating refrigerant during heating operation is HFC32: HFC125: HFC134.
a is (α-α ₁ ) :( β-β ₁ ) :( γ-γ ₁ ). On the other hand, the composition of the circulating refrigerant during cooling operation is HFC32 vs. HFC125.
Against HFC134a is (α-α ₂ ) :( β-β ₂ ) :( γ-
γ ₂ ) and the ratio of HFC32 is higher during heating operation.

Comparing the refrigerating capacities of the refrigerants, the refrigerating capacity of the circulating refrigerant is higher during the heating operation because the refrigerating capacity of the circulating refrigerant is HFC32, HFC124, and HFC134a.

Generally, in the case of an air conditioner, the refrigerating capacity required for heating operation is larger than the refrigerating capacity required for cooling operation, but in the refrigerating apparatus of the present invention, the generating capacity is changed by changing the composition of the circulating refrigerant. It can be varied, and efficiency can be improved.

Next, a third embodiment of the present invention will be described with reference to the drawings. FIG. 5 shows a third refrigerating apparatus of the present invention.
It is a refrigerating cycle figure in the Example of.

In the figure, 21 is a compressor, 22 is a condenser, 23 is a throttle device, and 24 is an annular evaporator connected to form a refrigeration cycle. 25 is a lubricating oil temperature controller.

FIGS. 6 (a) and 6 (b) are examples of diagrams showing the relationship between the dissolution rate of each refrigerant in the lubricating oil and the temperature and pressure.

In this refrigeration cycle, a case of heating operation using a non-azeotropic mixed refrigerant of HFC32 amount α and HFC134a amount β will be described first. The high-temperature and high-pressure refrigerant vapor compressed by the compressor 21 radiates heat in the condenser 22 and is condensed and liquefied. After that, the expansion device 23 decompresses and expands to become a gas-liquid two-phase refrigerant, which absorbs heat in the evaporator 24 and evaporates to become a refrigerant vapor, which is again sucked into the compressor 21.

At this time, a part of the lubricating oil in the refrigeration cycle circulates in the refrigeration cycle together with the refrigerant, but most of it remains inside the compressor 21. At that time, the temperature of the lubricating oil inside the compressor 21 is controlled by the lubricating oil temperature controller,
The pressure depends on the operating conditions, and the temperature and pressure are shown in Fig. 6.
In the states of P ₁ and T ₁ of (a) and (b), the corresponding amounts of the refrigerants are dissolved in the lubricating oil, so that the HFC32 in the refrigerant actually circulating in the refrigeration cycle
The quantity is (α-α ₁ ). The amount of HFC134a is (β-
β ₁ ).

Next, when the cooling operation is performed, the temperature and pressure inside the compressor 21 move to the states of P ₂ and T ₂ in FIGS. 6A and 6B, and the amount of the refrigerant dissolved in the lubricating oil is also changed. The amount of HFC32 in the refrigerant that has changed and is actually circulating in the refrigeration cycle is (α-
α ₂ ) and the amount of HFC134a becomes (β-β ₂ ).

Α shown in FIGS. 6A and 6B₁,
α₂, Β₁, Β₂As you can see, the circulating refrigerant during heating operation
The composition of HFC32 vs. HFC134a is (α-α₁):
(Β-β₁). On the other hand, the composition of the circulating refrigerant during the cooling operation is HF.
C32 vs. HFC134a is (α-α ₂): (Β-β₂)When
The ratio of HFC32 becomes higher during heating operation
There is. Comparing the refrigerating capacity of refrigerants
Since it is C32 and HFC134a, the refrigerating capacity of the circulating refrigerant
The power is higher during heating operation.

Generally, in the case of an air conditioner, the refrigerating capacity required in the heating operation is larger than the refrigerating capacity required in the cooling operation, but in the refrigerating apparatus of the present invention, the generating capacity is changed by changing the composition of the circulating refrigerant. It can be varied, and efficiency can be improved.

[0042]

As is apparent from the above embodiments, the refrigerating apparatus of the present invention constitutes a refrigerating cycle by connecting a compressor, a condenser, a throttle device and an evaporator in a ring, and a non-azeotropic refrigerant as a refrigerant. When two or more kinds of refrigerants are mixed and used, and when the amount of the refrigerant dissolved in the lubricating oil increases or decreases with changes in the temperature and pressure of the lubricating oil, the change characteristics have different characteristics for each used refrigerant. Using such a lubricating oil, a lubricating oil temperature controller that controls the temperature of the compressor and the condenser is provided, and the composition of the refrigerant actually circulating in the refrigeration cycle is changed to perform capacity control and performance improvement. It is possible to realize a refrigeration system capable of performing the above.

[Brief description of drawings]

FIG. 1 is a refrigeration cycle diagram according to a first embodiment of the present invention.

FIG. 2A is a diagram showing the relationship between the dissolution rate of a high-performance refrigerant in lubricating oil and the temperature and pressure in the first embodiment of the present invention. FIG. 2B is the first embodiment of the present invention. Diagram showing the relationship between the rate of dissolution of low-performance refrigerant in lubricating oil and the temperature and pressure in the example

FIG. 3 is a refrigeration cycle diagram in the second embodiment of the present invention.

FIG. 4A is a diagram showing the relationship between the dissolution rate of HFC32 in lubricating oil and the temperature and pressure in the second embodiment of the present invention, and FIG. 4B is the diagram of the second embodiment of the present invention. H into lubricating oil
The diagram (c) showing the relationship between the dissolution rate of FC125, temperature, and pressure is (H) in the lubricating oil in the second embodiment of the present invention.
Diagram showing the relationship between the dissolution rate of FC134a, temperature, and pressure

FIG. 5 is a refrigeration cycle diagram in the third embodiment of the present invention.

FIG. 6A is a diagram showing the relationship between the dissolution rate of HFC32 in lubricating oil and the temperature and pressure in the third embodiment of the present invention, and FIG. 6B is the diagram of the third embodiment of the present invention. H into lubricating oil
Diagram showing the relationship between the dissolution rate of FC134a, temperature, and pressure

FIG. 7 is a refrigeration cycle diagram of a conventional refrigerator.

[Explanation of symbols]

 1 Compressor 2 Condenser 3 Throttling device 4 Evaporator 5 Lubricating oil temperature controller

Continued Front Page (72) Inventor Yamaguchi Adult, 1006 Kadoma, Kadoma City, Osaka Prefecture Matsushita Electric Industrial Co., Ltd.

Claims (3)

[Claims] 1. A refrigeration cycle is constituted by connecting a compressor, a condenser, a throttle device, and an evaporator in a ring, and two or more kinds of non-azeotropic refrigerants containing no chlorine are mixed and used. When the amount of refrigerant dissolved in the lubricating oil increases or decreases as the temperature or pressure of the lubricating oil changes, use a lubricating oil whose change characteristics have different characteristics for each refrigerant used, and then compress A refrigeration system equipped with a lubricating oil temperature controller that controls the temperature of the lubricating oil inside the machine. 2. HFC32 / HFC125 / H as a refrigerant
The refrigeration system according to claim 1, wherein FC134a is used. 3. The refrigerating apparatus according to claim 1, wherein HFC32 / HFC134a is used as the refrigerant.