JP3368692B2 - Refrigeration system using non-azeotropic refrigerant mixture - Google Patents

Description

Detailed Description of the Invention

[0001]

This invention relates to a high boiling point refrigerant R22.
, A mixed refrigerant using R13B1 as a low boiling point refrigerant, HFC134a as a high boiling point refrigerant, a mixed refrigerant using HFC32 as a low boiling point refrigerant, or HFC134 as a high boiling point refrigerant.
a relates to a refrigerating apparatus that uses non-azeotropic mixed refrigerants such as a mixed refrigerant that uses HFC32 / 125 as a low boiling point refrigerant.

[0002]

2. Description of the Related Art Conventionally, a refrigerating apparatus using this kind of non-azeotropic mixed refrigerant can control its capacity by changing the composition ratio of a high boiling point refrigerant and a low boiling point refrigerant which are circulated in the refrigeration cycle system. Therefore, compared to the capacity control by the compressor unloader mechanism or the like, there is an advantage that the performance efficiency (COP) is less likely to decrease due to the decrease in load factor.

An example of such a refrigerating device is Japanese Patent Laid-Open No. 60-
There is one disclosed in Japanese Patent No. 142162. This is, as shown in FIG. 10, a compressor P, a condenser C, a first
A mixed refrigerant of a high-boiling-point refrigerant and a low-boiling-point refrigerant is enclosed in a refrigeration cycle system in which the second depressurizing mechanisms V1 and V2 and the evaporator E are sequentially connected, and the first and second depressurizing mechanisms V1 and V2 are included. A gas-liquid separator A for separating a condensate containing a large amount of high-boiling-point refrigerant and a non-condensable gas containing a large amount of low-boiling-point refrigerant is interposed in the intermediate pressure region between the two, and at the outlet of the evaporator E, Evaporator E
The tank part B for exchanging heat with the refrigerant on the outlet side is provided, and the upper gas region of the gas-liquid separator A and the tank part B are connected to the first opening / closing mechanism G.
1, and the tank B and the suction pipe L are connected via a second communication passage J2 having a second opening / closing mechanism G2.

Thus, by opening the first opening / closing mechanism G1 and closing the second opening / closing mechanism G2, the refrigerant containing a large amount of low boiling point refrigerant is liquefied and stored in the tank B, and the refrigerant containing a large amount of high boiling point refrigerant is circulated. I am trying to do low capacity driving. In addition, the first opening / closing mechanism G1 is closed and the second
By opening the opening / closing mechanism G2, the low boiling point refrigerant in the tank portion B is released into the system, and the refrigerant in a state in which the low boiling point refrigerant and the high boiling point refrigerant are mixed at a predetermined composition ratio is circulated to increase the temperature. I am trying to drive.

[0005]

However, in the non-azeotropic mixed refrigerant, the isotherms are not parallel to the horizontal axis as shown in the Mollier diagram of FIG. 11, and the inlet b of the evaporator E has the lowest temperature. The temperature of the refrigerant at the outlet b'of the evaporator E increases from the minimum temperature because the temperature increases as the degree of dryness increases as the evaporation progresses, and the low boiling point in the tank B is reached. Liquefaction of the refrigerant is slow and a time delay occurs in capacity control.
There is a problem that the holding pressure in the tank part B becomes relatively high and the amount of refrigerant that can be recovered from the gas-liquid separator A to the tank part B becomes small. Further, in order to avoid these, there is a problem that it is necessary to increase the capacity of the tank B or increase the amount of refrigerant charged in the refrigeration cycle.

The main object of the present invention is to promote the liquefaction of the low boiling point refrigerant in the tank without increasing the tank capacity and the refrigerant filling amount more than necessary, and to improve the followability of capacity control. The point is to provide a refrigerating apparatus using a non-azeotropic mixed refrigerant that can increase the amount of refrigerant that can be held in a tank and can expand the control range of capacity control.

[0007]

According to the present invention as set forth in claim 1, as shown in FIGS. 1 and 8, a compressor is used to efficiently separate a high-boiling-point refrigerant and a low-boiling-point refrigerant. In a refrigeration system using a non-azeotropic mixed refrigerant in which a mixed refrigerant of a high boiling point refrigerant and a low boiling point refrigerant is enclosed in a system of a refrigeration cycle in which condensation, decompression and evaporation are repeated, a condensate containing a large amount of a high boiling point refrigerant and A separation part (5) for separating the non-condensable gas containing a large amount of the low boiling point refrigerant, and a tank part (6) for exchanging heat with the low temperature refrigerant after depressurizing the condensate containing a large amount of the high boiling point refrigerant are provided. The upper gas region of (5) and the tank part (6) are connected via a first communication passage (81) having a first opening / closing mechanism (71), and the tank part (6) and the low-pressure part in the refrigeration cycle are connected. And the second opening / closing mechanism (72)
A shell (Sb) for generating hot water, a heat exchanger serving as a condenser connected through a second communication passage (82) having a shell, a refrigerant pipe (Tb) installed therein, and a refrigerant inlet / outlet header. (H1, H2) is an in-tube condensing type, and a separation section (5) for separating a condensate containing a large amount of high-boiling-point refrigerant and a non-condensable gas containing a large amount of low-boiling-point refrigerant is provided on the outlet side of the condensed refrigerant. This is a refrigeration system using a non-azeotropic mixed refrigerant that is the header (H2) of the above.

The present invention according to claim 2 enables not only holding of a low-boiling-point refrigerant but also holding of a high-boiling-point refrigerant, as shown in FIGS. 3, 4 and 8, and by changing a wide composition ratio. To further expand the control range of capacity control, compression, condensation,
In a refrigeration system using a non-azeotropic mixed refrigerant in which a mixed refrigerant of a high boiling point refrigerant and a low boiling point refrigerant is enclosed in a system of a refrigeration cycle in which decompression and evaporation are repeated, a condensate containing a high boiling point refrigerant and a low boiling point refrigerant A separation part (5) for separating the non-condensed gas containing a large amount of gas and a tank part (6) for exchanging heat with the low temperature refrigerant after decompressing the condensed liquid containing a large amount of the high boiling point refrigerant, and the separation part (5) The upper gas area and the tank part (6) of
A second communication passage having a second opening / closing mechanism (72), which is connected through a first communication passage (81) having a first opening / closing mechanism (71) and connects the tank portion (6) and the low-pressure portion in the refrigeration cycle. (82) is connected to separate the non-evaporated liquid containing a large amount of high-boiling-point refrigerant and the evaporated gas containing a large amount of low-boiling-point refrigerant to store the non-evaporated liquid containing a large amount of high-boiling-point refrigerant, and a low-pressure tank having a predetermined capacity. (90) is provided, and the lower part of the low-pressure tank (90) and the suction part of the compressor are connected via a third communication passage (83) having a third opening / closing mechanism (73) to form a heat that becomes a condenser. The exchanger has a shell (Sb) for generating hot water, a refrigerant pipe (Tb) installed therein, and a refrigerant inlet / outlet header (H).
1, H2) is a pipe condensation type, and a separation part (5) for separating a condensate containing a large amount of high-boiling-point refrigerant and a non-condensable gas containing a large amount of low-boiling-point refrigerant is located on the condensed refrigerant outlet side. It is a refrigerating device using a non-azeotropic mixed refrigerant which is a header (H2).

The present invention according to claim 3 is based on FIG. 5 and FIG.
As shown in Fig. 1, one tank portion 6 is also used so that not only the low boiling point refrigerant but also the high boiling point refrigerant can be held in place of the low boiling point refrigerant, and a wide range of composition ratios can be changed to control the capacity control range. In order to further expand the above, in a refrigeration cycle system in which compression, condensation, decompression and evaporation are repeated, a refrigeration system using a non-azeotropic mixed refrigerant in which a mixed refrigerant of a high boiling point refrigerant and a low boiling point refrigerant is enclosed, has a high boiling point. Separation unit (5) for separating a condensate containing a large amount of refrigerant and a non-condensing gas containing a large amount of a low boiling point refrigerant
And a tank part (6) for exchanging heat with the low temperature refrigerant after depressurizing the condensate containing a large amount of high boiling point refrigerant, and the upper gas region of the separation part (5) and the tank part (6) are The tank part (6) and the low-pressure part in the refrigeration cycle are connected to each other via the first communication path (81) having the opening / closing mechanism (71), and the second communication path (82) having the second opening / closing mechanism (72). )
And a low-pressure separation section (9) for separating the non-evaporated liquid containing a large amount of high-boiling-point refrigerant and the evaporative gas containing a large amount of low-boiling-point refrigerant, the lower part of the low-pressure separation section (9) and the tank section ( 6) via a third communication passage (83) having a non-return mechanism (70) that allows only the flow from the low-pressure separation section (9) to the tank section (6) and a third opening / closing mechanism (73). And a low pressure part in the refrigeration cycle are connected via a fourth pressure equalizing fourth communication passage (84) having a fourth opening / closing mechanism (74), and a condenser is connected. The heat exchanger is an in-tube condensation type having a shell (Sb) for generating hot water, a refrigerant pipe (Tb) installed therein, and a refrigerant inlet / outlet header (H1, H2). Separation that separates a condensate rich in boiling point refrigerant and a non-condensable gas rich in low boiling point refrigerant (5) is a refrigeration apparatus using a non-azeotropic refrigerant which is take-out side of the header (H2) of the condensing refrigerant.

[0010]

[0011]

[0012]

The present invention according to claim 4 is based on FIG. 5 and FIG.
As described above, in order to efficiently separate the high-boiling-point refrigerant and the low-boiling-point refrigerant using the evaporator, compression, condensation, decompression and evaporation are repeated in the refrigeration cycle system, and the high-boiling-point refrigerant and the low-boiling-point refrigerant are combined. In a refrigerating apparatus using a non-azeotropic mixed refrigerant in which a mixed refrigerant is sealed, a separation unit (5) for separating a condensate containing a large amount of a high boiling point refrigerant and a non-condensing gas containing a large amount of a low boiling point refrigerant.
And a tank section (6) for exchanging heat with the low-temperature refrigerant after depressurizing the condensate containing a large amount of high-boiling-point refrigerant, and the upper gas region of the separation section (5) and the tank section (6) The tank part (6) and the low-pressure part in the refrigeration cycle are connected to each other via the first communication path (81) having the opening / closing mechanism (71), and the second communication path (82) having the second opening / closing mechanism (72). )
And a low-pressure separation section (9) for separating the non-evaporated liquid containing a large amount of high-boiling-point refrigerant and the evaporative gas containing a large amount of low-boiling-point refrigerant, the lower part of the low-pressure separation section (9) and the tank section ( 6) via a third communication passage (83) having a non-return mechanism (70) that allows only the flow from the low-pressure separation section (9) to the tank section (6) and a third opening / closing mechanism (73). And an upper gas region of the tank part (6) and a low pressure part in the refrigeration cycle are connected via a fourth pressure equalizing fourth communication passage (84) having a fourth opening / closing mechanism (74), and the evaporator is connected. The heat exchanger to be used is an in-tube evaporation type having a shell (Sb) for generating cold water, a refrigerant pipe (Tb) installed therein, and a refrigerant inlet / outlet header (H1, H2). Low pressure that separates non-evaporated liquid that contains a large amount of boiling point refrigerant and evaporative gas that contains a large amount of low boiling point refrigerant Away portion (9) is a refrigeration apparatus using a non-azeotropic refrigerant which is take-out side of the header (H1) of the evaporating refrigerant.

The present invention according to claim 5 is, as shown in FIG.
In a relatively large-scale separate air heat source heat pump system such as a building air conditioner, the tank portion 6 can be sufficiently cooled even when there is a pressure increase corresponding to the liquid head at the outlet portion of the decompression mechanism 3 of the main refrigerant circuit. Therefore, the tank portion (6) exchanges heat with the low temperature refrigerant whose pressure is reduced by the pressure reducing means (30) provided separately from the pressure reducing mechanism (3) of the main refrigerant circuit.

[0015]

In the invention described in claim 1, as shown in FIG.
When performing low capacity operation, the first opening / closing mechanism 71 is opened and the second opening / closing mechanism 72 is closed. Thereby, the separating unit 5
Then, the non-condensed gas c containing a large amount of the low boiling point refrigerant separated from the condensate a ′ containing a large amount of the high boiling point refrigerant flows into the tank portion 6 through the first communication passage 81, and in the tank portion 6, the high boiling point The condensed liquid containing a large amount of refrigerant is cooled by the low temperature refrigerant b after being decompressed, and is liquefied and stored inside the tank unit 6. In this way, the refrigerant containing a large amount of the high boiling point refrigerant circulates in the refrigeration cycle, and low capacity operation can be performed.

On the other hand, when performing high-capacity operation, the first opening / closing mechanism 71 is closed and the second opening / closing mechanism 72 is opened, so that the low boiling point component stored in the tank portion 6 is the second communication passage 8
After being discharged into the system of the refrigeration cycle via 2, the refrigerant in a state where the low boiling point refrigerant and the high boiling point refrigerant are mixed at a predetermined composition ratio circulates, and high capacity operation can be performed.

During low capacity operation in which the tank portion 6 holds a low boiling point component, as shown in FIG. 2, the low temperature refrigerant b after depressurizing the condensate containing a large amount of the high boiling point refrigerant in the tank portion 6, that is, Since the refrigerant b containing the low boiling point refrigerant is cooled by the lowest temperature refrigerant b before passing through the evaporator, the liquefaction of the low boiling point component in the tank portion 6 can be promoted.

Moreover, since the refrigerant is cooled with the lowest temperature in this way, the condensate saturation pressure e of the low boiling point component in the tank portion 6 can be lowered, and the low boiling point refrigerant that can be held in the tank portion 6 can be increased. That is, as the recovery of the low-boiling-point refrigerant from the separation section 5 to the tank section 6 progresses, the composition of the circulating refrigerant in the refrigeration cycle shifts to the high-boiling-point component side, and the condensing temperature is considered to be constant. The condensation pressure of is decreasing (Fig. 2
At, a ′ drops in pressure to a ″). When cooling with the conventional evaporator outlet refrigerant b ', the saturation pressure d in the tank part
Is relatively high and the pressure a ″ in the separation section becomes equal to this saturation pressure d, the outflow from the separation section to the tank section stops, but in this invention, the saturation pressure e in the tank section 6 is low. As a result, a larger amount of the low boiling point component can be flown into the tank portion 6, and the amount of the low boiling point component that can be held in the tank portion 6 can be increased.

In this way, the liquefaction of the low boiling point refrigerant in the tank portion 6 can be promoted without increasing the capacity of the tank portion 6 or the amount of refrigerant filled in the refrigeration cycle system more than necessary, and the ability control followability can be improved. It is possible to increase the amount of refrigerant that can be retained in the tank portion 6 and to expand the control range of capacity control. Further, as shown in FIG. 8, in the header H2 on the condensed refrigerant outlet side of the in-tube condenser, a condensate containing a large amount of high-boiling point refrigerant and a non-condensing gas containing a large amount of a low-boiling point refrigerant can be separated, Even if the gas-liquid separator is not used, the in-pipe condenser can be used to efficiently separate the high boiling point refrigerant and the low boiling point refrigerant, and the structure can be simplified accordingly.

According to the second aspect of the invention, as shown in FIGS. 3 and 4, the low pressure tank 90 contains a large amount of high boiling point refrigerant by controlling the humidity of the refrigerant b'on the outlet side of the evaporator. The non-evaporated liquid f can be separated and stored from the evaporated gas containing a large amount of the low boiling point refrigerant. Third opening / closing mechanism 73
The high-boiling point component can be retained in the low-pressure tank 90 when closed, and the high-boiling point component in the low-pressure tank 90 can be released into the system of the refrigeration cycle when the third opening / closing mechanism 73 is opened. Thus, in addition to holding and releasing the low-boiling point component in the tank portion 6, the holding and releasing of the high-boiling point component in the low-pressure tank 90 can also be performed, and a wide range of composition ratios can be changed, further increasing the control range of capacity control. Can be expanded.

According to the third aspect of the invention, as shown in FIG. 5, the first opening / closing mechanism 71 is opened and the second to fourth opening / closing mechanisms 7 are opened.
By closing 2, 73, 74, the low boiling point component can be retained in the tank portion 6, the second opening / closing mechanism 72 is opened, and the first, third, and fourth opening / closing mechanisms 71, 73, 74 are closed. As a result, the low boiling point component held in the tank portion 6 can be released into the system of the refrigeration cycle. Further, by controlling the humidity of the refrigerant on the outlet side of the evaporator, the low-pressure separation section 9 can separate the non-evaporated liquid containing a large amount of the high-boiling-point refrigerant and the evaporated gas containing a large amount of the low-boiling-point refrigerant. The mechanism 74 is opened to equalize the tank portion 6 to a low pressure and the third
The opening / closing mechanism 73 is opened, and the first and second opening / closing mechanisms 71, 7 are further opened.
By closing 2, the high boiling point component separated in the low pressure separation unit 9 can be retained in the tank unit 6, and by opening the second opening / closing mechanism 72, the high boiling point component retained in the tank unit 6 can be retained. It can be released into the system of the refrigeration cycle. In this way, the low boiling point refrigerant and the high boiling point refrigerant can be selectively retained in one tank portion 6, and it is possible to change a wide range of composition ratios while keeping the number of containers having a large capacity to a minimum. Can be further expanded.

[0022]

[0023]

[0024]

According to the fourth aspect of the present invention, as shown in FIG. 8 as well, the header H on the take-out side of the evaporated refrigerant of the in-pipe evaporator is shown.
In No. 1, it is possible to separate the non-evaporated liquid containing a large amount of high-boiling-point refrigerant and the evaporative gas containing a large amount of low-boiling-point refrigerant. The boiling point refrigerant can be efficiently separated, and the structure can be simplified accordingly.

In a fifth aspect of the present invention, as shown in FIG. 9, in a relatively large-scale separate air heat source heat pump system for building air conditioning, etc., the outlet portion of the pressure reducing mechanism 3 of the main refrigerant circuit corresponds to a liquid head. If there is an increase in pressure, the temperature of the outlet side refrigerant of the pressure reducing mechanism 3 is high, but the pressure reducing means 30 provided separately from the pressure reducing mechanism 3 of the main refrigerant circuit does not cool the tank portion 6 with such a refrigerant. Since the low temperature refrigerant is cooled to cool the tank portion 6, the tank portion 6 can be sufficiently cooled, the liquefaction of the low boiling point component in the tank portion 6 can be promoted, and the amount thereof can be increased.

[0027]

FIG. 1 shows a heat pump type refrigerating apparatus according to a first embodiment, which includes a compressor 1, a four-way switching valve 10, a heat source side heat exchanger 2, a gas-liquid separator 51, a pressure reducing mechanism 3, and a use. The side heat exchangers 4 are sequentially connected by a refrigerant pipe. 11, 12, 1
Reference numerals 3 and 14 denote rectification check mechanisms that control the flow of the refrigerant in accordance with cooling and heating. In the refrigeration cycle system,
R22 as a high boiling point refrigerant and R13B1 as a low boiling point refrigerant
HFC as a mixed refrigerant or high boiling point refrigerant
134a is a mixed refrigerant using HFC32 as a low boiling point refrigerant, or HFC134 as a high boiling point refrigerant.
A mixed refrigerant or the like using HFC32 / 125 as a low boiling point refrigerant is enclosed.

During cooling, as indicated by the solid line arrow in FIG.
Chasing by the code, 1, 10, 2, 11, 51, 3, 12,
Refrigerant is caused to flow in the order of 4, 10, 1 and the heat source side heat exchanger 2 is used as a condenser and the use side heat exchanger 4 is used as an evaporator.

During heating, as indicated by the dotted arrow in FIG.
Chasing by code, 1, 10, 4, 13, 51, 3, 14,
Refrigerant is caused to flow in the order of 2, 10, 1 and the use side heat exchanger 4 is used as a condenser and the heat source side heat exchanger 2 is used as an evaporator.

In the above structure, the gas-liquid separator 51 constitutes the separation section 5 for separating the condensate containing a large amount of the high boiling point refrigerant and the non-condensing gas containing a large amount of the low boiling point refrigerant. or,
A tank portion 6 having a predetermined capacity is provided at the outlet of the decompression mechanism 3,
Inside the tank section 6, a heat exchange tube 60 is provided through which the low-temperature refrigerant b, which has been decompressed by the decompression mechanism 3, flows. And, the upper gas region of the gas-liquid separator 51 and the tank portion 6 which form the separation portion 5 are provided with a first opening / closing mechanism 71 including a solenoid valve or the like.
The tank portion 6 and the outlet-side low-pressure portion of the heat exchange pipe 60 are connected to each other via the communication passage 81 via a second communication passage 82 having a second opening / closing mechanism 72 also including an electromagnetic valve or the like.

Thus, both during cooling and during heating,
By opening the first opening / closing mechanism 71 and closing the second opening / closing mechanism 72, the low boiling point component is held inside the tank portion 6 and low capacity operation can be performed. On the other hand, while closing the first opening / closing mechanism 71, the second opening / closing mechanism 7
By opening 2, the low boiling point component stored in the tank 6 is released into the system of the refrigeration cycle, and high capacity operation can be performed. During low-capacity operation, the tank portion 6 is cooled by the lowest temperature refrigerant b before passing through the evaporator 4 or 2. Therefore, the liquefaction of the low boiling point component in the tank portion 6 can be promoted and stored. The amount of low boiling point components can be increased.

FIG. 3 shows a second embodiment, which is different from FIG. 1 in that the non-evaporated liquid containing a large amount of high boiling point refrigerant and the evaporative gas containing a large amount of low boiling point refrigerant are separated on the suction side of the compressor 1. Then, a low-pressure tank 90 having a predetermined capacity for storing the non-evaporated liquid containing a large amount of high-boiling-point refrigerant is provided. The point is that they are connected via a third communication passage 83 having a. In this case, the low boiling point refrigerant can be retained in the low pressure tank 90 by controlling the wetness of the outlet of the evaporator 4 or 2, and the control range can be further expanded.

FIG. 5 shows the third embodiment, and is different from FIG. 3 in that the low boiling point component and the high boiling point component are selectively stored in one tank portion 6. That is, the suction side of the compressor 1 is provided with a low-pressure separation section 9 having a relatively small capacity for separating the non-evaporated liquid containing a large amount of high-boiling-point refrigerant and the evaporative gas containing a large amount of low-boiling-point refrigerant. The lower portion of the portion 9 and the tank portion 6 are connected via a third communication passage 83 having a check mechanism 70 for allowing only the flow from the low pressure separation portion 9 to the tank portion 6 and a third opening / closing mechanism 73 formed of a solenoid valve. In addition, the upper gas region of the tank portion 6 and the low pressure portion in the refrigeration cycle are connected via a fourth pressure equalizing fourth communication passage 84 having a fourth opening / closing mechanism 74 including an electromagnetic valve or the like.

FIG. 6 shows the structure on which the present invention is based,
The heat exchanger 2 serving as a condenser is provided with a shell Sa for releasing the refrigerant.
And a cooling water pipe Ta installed therein, which is of the outside condensation type. It is possible to separate a condensate containing a large amount of high-boiling-point refrigerant and a non-condensable gas containing a large amount of low-boiling-point refrigerant inside the shell Sa of this extra-condenser, and therefore, using this shell Sa, The separation unit 5 is configured to separate the condensate containing a large amount of the high boiling point refrigerant and the non-condensable gas containing a large amount of the low boiling point refrigerant. Further, the heat exchanger 4 serving as an evaporator is provided with a shell Sb for generating cold water,
The in-tube evaporation type is provided with a refrigerant pipe Tb installed therein and headers H1 and H2 for taking in and out the refrigerant.
Header H on the take-out side of the evaporated refrigerant in this in-pipe evaporator
In the inside of 1, it is possible to separate the non-evaporated liquid containing a large amount of high-boiling-point refrigerant and the evaporative gas containing a large amount of low-boiling-point refrigerant.
1 is used to configure the low-pressure separation unit 9 for separating the non-evaporated liquid containing a large amount of high-boiling-point refrigerant and the evaporated gas containing a large amount of low-boiling-point refrigerant.

FIG. 7 shows another precondition of the present invention, which is applied to an air heat source heat pump chiller / heater. In this configuration, an air heat exchanger with a fan 20 is used as the heat source side heat exchanger 2, and a shell Sb for generating cold water or hot water is used for the use side heat exchanger 4, a refrigerant pipe Tb installed therein, and A water heat exchanger having headers H1 and H2 for taking in and out the refrigerant is used.

FIG. 8 shows the fourth embodiment, and the difference from FIG. 7 is that the utilization side heat exchanger 4 is used to configure the separation section 5 and the low pressure separation section 9. That is, the usage-side heat exchanger 4 includes a shell Sb that produces cold water or hot water, a refrigerant pipe Tb that is installed inside the shell Sb, and a header H for taking in and out the refrigerant.
1, H2, when the utilization side heat exchanger 4 is used as a condenser, the condensed refrigerant outlet side header H
In the inside of 2, it is possible to separate the condensate containing a large amount of high-boiling-point refrigerant and the non-condensable gas containing a large amount of low-boiling-point refrigerant. The separation unit 5 for separating the liquid and the non-condensable gas containing a large amount of the low boiling point refrigerant is configured.
When the utilization side heat exchanger 4 is used as an evaporator, the non-evaporated liquid containing a large amount of the high boiling point refrigerant and the evaporative gas containing a large amount of the low boiling point refrigerant are separated inside the header H1 on the extraction side of the evaporated refrigerant. Therefore, the low-pressure separation section 9 for separating the non-evaporated liquid containing a large amount of high-boiling point refrigerant and the evaporative gas containing a large amount of low-boiling point refrigerant is formed by utilizing the header H1 on the extraction side of the evaporating refrigerant. I have decided.

FIG. 9 shows a fifth embodiment, in which a heat source side heat exchanger 2 constituted by an air heat exchanger provided with a fan 20 is installed on the roof of a building, and the others are installed in a basement or the like, such as a building air conditioner. It is a relatively large separate air source heat pump system. Since this structure has a pressure increase corresponding to the liquid head at the outlet of the depressurizing mechanism 3 of the main refrigerant circuit, the tank unit 6 is decompressed by the low temperature refrigerant depressurized by the depressurizing means 30 provided separately from the depressurizing mechanism 3 of the main refrigerant circuit. It was made to cool.

[0038]

According to the invention described in claim 1, even if the capacity of the tank portion 6 or the amount of refrigerant filled in the refrigeration cycle system is not increased more than necessary, the low boiling point refrigerant in the tank portion 6 Liquefaction can be promoted, followability of capacity control can be improved, and the amount of refrigerant that can be retained in the tank portion 6 can be increased, so that the control range of capacity control can be expanded. Also,
Even without using a gas-liquid separator, it is possible to efficiently separate a high boiling point refrigerant and a low boiling point refrigerant using the header H2 on the condensed refrigerant outlet side of the in-tube condenser, and to simplify the structure accordingly. You can

According to the second aspect of the invention, the tank portion 6
In addition to holding and releasing low-boiling components in the low-pressure tank 90, holding and releasing high-boiling components in the low-pressure tank 90 can be performed, a wide range of composition ratios can be changed, and the control range of capacity control can be further expanded. .

According to the third aspect of the present invention, the low boiling point refrigerant and the high boiling point refrigerant can be selectively retained in one tank portion 6, and a wide composition ratio can be achieved while minimizing the number of vessels having a large capacity. Can be changed, and the control range of capacity control can be further expanded.

[0041]

[0042]

[0043]

According to the fourth aspect of the present invention, the high boiling point refrigerant and the low boiling point refrigerant are efficiently separated by utilizing the header H1 on the take-out side of the evaporated refrigerant of the in-pipe evaporator without using a special low pressure tank or the like. The configuration can be simplified accordingly.

According to the fifth aspect of the invention, the decompression means 30 provided separately from the decompression mechanism 3 of the main refrigerant circuit allows the decompression of the main refrigerant circuit in a relatively large-scale separate air heat source heat pump system for building air conditioning. Even when there is a pressure increase corresponding to the liquid head at the outlet of the mechanism 3, the tank 6
Can be sufficiently cooled, the liquefaction of the low boiling point component in the tank part 6 can be promoted, and the amount of the low boiling point component held can be increased.

[Brief description of drawings]

FIG. 1 is a piping diagram of a first embodiment of the present invention.

FIG. 2 is an explanatory view of the operation of the first embodiment.

FIG. 3 is a piping diagram of the second embodiment.

FIG. 4 is an explanatory view of the operation of the second embodiment.

FIG. 5 is a piping diagram of the third embodiment.

FIG. 6 is a piping diagram of a configuration that is a premise of the present invention.

FIG. 7 is a piping diagram of a configuration that is another prerequisite of the present invention.

FIG. 8 is a piping diagram of the sixth embodiment.

FIG. 9 is a piping diagram of the seventh embodiment.

FIG. 10 is a piping diagram of a conventional example.

FIG. 11 is an explanatory diagram of conventional problems.

[Explanation of symbols]

3 decompression mechanism 5 Separation section 6 tank section 9 Low pressure separation section 30 decompression means 51 gas-liquid separator 70 Non-return mechanism 71 First opening / closing mechanism 72 Second opening / closing mechanism 73 Third opening / closing mechanism 74 4th opening / closing mechanism 81 First passage 82 Second passage 83 Third communication passage 84 4th passage H1, H2 header Sa, Sb shell Ta cooling water piping Tb refrigerant pipe

─────────────────────────────────────────────────── ─── Continued Front Page (58) Fields surveyed (Int.Cl. ⁷ , DB name) F25B 1/00 395

Claims (5)

(57) [Claims] 1. A refrigeration system using a non-azeotropic mixed refrigerant in which a mixed refrigerant of a high boiling point refrigerant and a low boiling point refrigerant is enclosed in a refrigeration cycle system in which compression, condensation, decompression and evaporation are repeated, Separation part (5) for separating a condensed liquid containing a large amount of high boiling point refrigerant and non-condensed gas containing a large amount of low boiling point refrigerant, and a tank part (6) for exchanging heat with the low temperature refrigerant after depressurizing the condensed liquid containing a large amount of high boiling point refrigerant And the upper gas region of the separation part (5) and the tank part (6) are connected via the first communication passage (81) having the first opening / closing mechanism (71), and the tank part (6) is provided. And a low pressure part in the refrigeration cycle are connected via a second communication passage (82) having a second opening / closing mechanism (72), and a heat exchanger as a condenser forms a shell (S
b), a refrigerant pipe (Tb) installed therein, and a refrigerant inlet / outlet header (H1, H2) in-tube condensing type, which contains a large amount of a high-boiling-point condensate and a low-boiling-point refrigerant. A refrigeration system using a non-azeotropic mixed refrigerant in which a separation section (5) for separating the non-condensed gas contained therein is a header (H2) on the extraction side of the condensed refrigerant. 2. A high boiling point refrigerant in a refrigeration system using a non-azeotropic mixed refrigerant in which a mixed refrigerant of a high boiling point refrigerant and a low boiling point refrigerant is enclosed in a refrigeration cycle system in which compression, condensation, decompression and evaporation are repeated. Separation part (5) for separating a condensed liquid containing a large amount of high boiling point refrigerant and non-condensed gas containing a large amount of low boiling point refrigerant, and a tank part (6) for exchanging heat with the low temperature refrigerant after depressurizing the condensed liquid containing a large amount of high boiling point refrigerant And the upper gas region of the separation part (5) and the tank part (6) are connected via the first communication passage (81) having the first opening / closing mechanism (71), and the tank part (6) is provided. And a low pressure part in the refrigeration cycle are connected via a second communication passage (82) having a second opening / closing mechanism (72), and a non-evaporated liquid containing a large amount of high boiling point refrigerant and an evaporated gas containing a large amount of low boiling point refrigerant. A predetermined volume to store the non-evaporated liquid containing a large amount of high boiling point refrigerant. Provided the low-pressure tank (90), and a suction portion of the lower and the compressor of the low-pressure tank (90), third
A shell (S) which is connected via a third communication passage (83) having an opening / closing mechanism (73) and which serves as a condenser forms a hot water.
b), a refrigerant pipe (Tb) installed therein, and a refrigerant inlet / outlet header (H1, H2) in-tube condensing type, which contains a large amount of a high-boiling-point condensate and a low-boiling-point refrigerant. A refrigeration system using a non-azeotropic mixed refrigerant in which a separation section (5) for separating the non-condensed gas contained therein is a header (H2) on the extraction side of the condensed refrigerant. 3. A high boiling point refrigerant in a refrigeration system using a non-azeotropic mixed refrigerant in which a mixed refrigerant of a high boiling point refrigerant and a low boiling point refrigerant is enclosed in a refrigeration cycle system in which compression, condensation, decompression and evaporation are repeated. Separation part (5) for separating a condensed liquid containing a large amount of high boiling point refrigerant and non-condensed gas containing a large amount of low boiling point refrigerant, and a tank part (6) for exchanging heat with the low temperature refrigerant after depressurizing the condensed liquid containing a large amount of high boiling point refrigerant And the upper gas region of the separation part (5) and the tank part (6) are connected via the first communication passage (81) having the first opening / closing mechanism (71), and the tank part (6) is provided. And a low pressure part in the refrigeration cycle are connected via a second communication passage (82) having a second opening / closing mechanism (72), and a non-evaporated liquid containing a large amount of high boiling point refrigerant and an evaporated gas containing a large amount of low boiling point refrigerant. A low pressure separation part (9) for separating the Lower tank portion (6) and the third with a low-pressure separation section check mechanism (70) and the third opening and closing mechanism (73) for permitting only flow from (9) tank section (6)
The upper gas region of the tank portion (6) and the low-pressure portion in the refrigeration cycle are connected to each other via the communication passageway (83), and the fourth communication passageway (84) for pressure equalization having the fourth opening / closing mechanism (74) is provided. A heat exchanger, which is connected via a shell and serves as a condenser, forms a shell (S
b), a refrigerant pipe (Tb) installed therein, and a refrigerant inlet / outlet header (H1, H2) in-tube condensing type, which contains a large amount of a high-boiling-point condensate and a low-boiling-point refrigerant. A refrigeration system using a non-azeotropic mixed refrigerant in which a separation section (5) for separating the non-condensed gas contained therein is a header (H2) on the extraction side of the condensed refrigerant. 4. A refrigeration system using a non-azeotropic mixed refrigerant in which a mixed refrigerant of a high boiling point refrigerant and a low boiling point refrigerant is enclosed in a refrigeration cycle system in which compression, condensation, decompression and evaporation are repeated, Separation part (5) for separating a condensed liquid containing a large amount of high boiling point refrigerant and non-condensed gas containing a large amount of low boiling point refrigerant, and a tank part (6) for exchanging heat with the low temperature refrigerant after depressurizing the condensed liquid containing a large amount of high boiling point refrigerant And the upper gas region of the separation part (5) and the tank part (6) are connected via the first communication passage (81) having the first opening / closing mechanism (71), and the tank part (6) is provided. And a low pressure part in the refrigeration cycle are connected via a second communication passage (82) having a second opening / closing mechanism (72), and a non-evaporated liquid containing a large amount of high boiling point refrigerant and an evaporated gas containing a large amount of low boiling point refrigerant. A low pressure separation part (9) for separating the Lower tank portion (6) and the third with a low-pressure separation section check mechanism (70) and the third opening and closing mechanism (73) for permitting only flow from (9) tank section (6)
The upper gas region of the tank portion (6) and the low-pressure portion in the refrigeration cycle are connected to each other via the communication passageway (83), and the fourth communication passageway (84) for pressure equalization having the fourth opening / closing mechanism (74) is provided. A heat exchanger, which is connected via the shell and serves as an evaporator, forms a shell (S
b), a refrigerant pipe (Tb) installed therein, and a refrigerant inlet / outlet header (H1, H2), which is an in-tube evaporative type, which is used for the non-evaporated liquid containing a large amount of high-boiling-point refrigerant and the low-boiling-point refrigerant. Low-pressure separation part (9) for separating evaporative gas containing much
Is a refrigeration system using a non-azeotropic mixed refrigerant that is a header (H1) on the extraction side of the evaporated refrigerant. 5. The tank section (6) exchanges heat with a low-temperature refrigerant whose pressure is reduced by a pressure reducing means (30) provided separately from the pressure reducing mechanism (3) of the main refrigerant circuit. A refrigeration system using the non-azeotropic mixed refrigerant as described above.