JP2015210070A - Complex air-conditioning refrigeration system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To further facilitate taking advantage of natural energy.SOLUTION: By using a complex cycle constituted by a first cycle being a refrigeration cycle of a reverse carnot cycle, and a second cycle being a refrigerant cycle, unused heat energy, which was conventionally wasted, is used by the heat exchange with refrigerant of the second cycle. In the cooling operation, refrigerant which passes through an expansion valve or expander and performs cooling operation by means of an indoor heat exchanger, thereby having low pressure and low temperature, and refrigerant of the second cycle are heat-exchanged to lower the temperature of the refrigerant of the second cycle. In addition, refrigerant which is compressed by the compressor of the first cycle, thereby having high pressure and high temperature, is heat-exchanged again with the refrigerant of the second cycle having the lowered temperature to lower the condensation temperature of the refrigerant of the first cycle so as to significantly reduce drive force required for a compressor in the first cycle.

Description

The present invention, using a combined cycle consisting of a first cycle of a reverse Carnot cycle and a second cycle of a refrigerant cycle, has been conventionally released from the condenser to the atmosphere only for cooling and discarded. Unused thermal energy is utilized by heat exchange with the refrigerant in the second cycle.
In the case of cooling, the second cycle is obtained by heat exchange between the refrigerant that has passed through the expansion valve or the expander of the first cycle and further cooled by the indoor heat exchanger to become low pressure and low temperature and the refrigerant of the second cycle. The refrigerant is cooled down. Then, the refrigerant that has been compressed by the compressor in the first cycle and becomes high pressure and high temperature is again heat exchanged with the refrigerant in the second cycle that has been cooled down, thereby reducing the condensation temperature of the refrigerant in the first cycle. The driving force required for the compressor is greatly reduced.
In the case of heating, the refrigerant of the second cycle is heated by heat exchange using the refrigerant that has been compressed by the compressor of the first cycle and has become high pressure and high temperature. The first cycle refrigerant evaporating temperature is increased by exchanging heat again between the refrigerant that has passed through the first cycle expansion valve or the expander and has become low pressure and low temperature and the second cycle refrigerant that has been heated. The driving force required for the compressor in the first cycle is greatly reduced.
In addition, an expander is attached instead of the expansion valve in the first cycle, and electric power is generated using the driving force to assist in driving the compressor in the first cycle and the circulation pump in the second cycle. Thus, the present invention relates to a composite air-conditioning refrigeration apparatus that can significantly reduce the power consumption of the air-conditioning and refrigeration apparatus.

Currently, air-conditioning refrigeration systems based on the reverse Carnot cycle are a powerful trump card for future low-carbon societies because of their high energy efficiency. In addition, the technology of air-conditioning refrigeration equipment in Japan has been steadily developing and has led the world. In such an environment, further improvement in performance of the air-conditioning refrigeration apparatus and effective use of the air-conditioning and refrigeration apparatus technology are required.

In such an environment, the social significance of an air-conditioning refrigeration system that utilizes the reverse Carnot cycle refrigeration cycle and the refrigerant cycle in a complex and skillful manner is immeasurable.

Patent 2546868 Patent 5441844

The present invention, using a combined cycle consisting of a first cycle of a reverse Carnot cycle and a second cycle of a refrigerant cycle, has been conventionally released from the condenser to the atmosphere only for cooling and discarded. Unused thermal energy is utilized by heat exchange with the refrigerant in the second cycle.
In the case of cooling, the second cycle is obtained by heat exchange between the refrigerant that has passed through the expansion valve or the expander of the first cycle and further cooled by the indoor heat exchanger to become low pressure and low temperature and the refrigerant of the second cycle. The refrigerant is cooled down. Then, the refrigerant that has been compressed by the compressor in the first cycle and becomes high pressure and high temperature is again heat exchanged with the refrigerant in the second cycle that has been cooled down, thereby reducing the condensation temperature of the refrigerant in the first cycle. The driving force required for the compressor is greatly reduced.
In the case of heating, the refrigerant of the second cycle is heated by heat exchange using the refrigerant that has been compressed by the compressor of the first cycle and has become high pressure and high temperature. The first cycle refrigerant evaporating temperature is increased by exchanging heat again between the refrigerant that has passed through the first cycle expansion valve or the expander and has become low pressure and low temperature and the second cycle refrigerant that has been heated. The driving force required for the compressor in the first cycle is greatly reduced.
In addition, an expander is attached instead of the expansion valve in the first cycle, and electric power is generated using the driving force to assist in driving the compressor in the first cycle and the circulation pump in the second cycle. Thereby, it is a composite air-conditioning refrigeration apparatus which can reduce the power consumption of an air-conditioning and refrigeration apparatus significantly.

Currently, electricity is generated by large-scale power generation facilities, or by private power generation in factories, etc., and individual small-scale power generation in each home, but nuclear power, which is large-scale power generation, is damaged during an accident. There is a problem of the size and construction location of hydropower and renewable energy such as geothermal, solar heat, solar and wind power. In-house power generation at factories also has problems such as CO2 emissions and fuel price fluctuations, and the use of renewable energy such as solar and wind power at each home is both unstable and unstable depending on the climate. It is done. In such a situation, it is necessary to further promote the effective use of energy.

The present invention, using a combined cycle consisting of a first cycle of a reverse Carnot cycle and a second cycle of a refrigerant cycle, has been conventionally released from the condenser to the atmosphere only for cooling and discarded. Unused thermal energy is utilized by heat exchange with the refrigerant in the second cycle.
A combined air-conditioning refrigeration system that can improve the overall air-conditioning refrigeration capacity and air-conditioning refrigeration efficiency in cooling and heating by skillfully exchanging and using the refrigerant in the first cycle and the refrigerant in the second cycle. In addition, an expander is attached instead of the expansion valve of the first cycle, and electric power is generated using the driving force to assist the drive of the compressor of the first cycle and the circulation pump of the second cycle. Thereby, it is a composite air-conditioning refrigeration apparatus which can reduce the power consumption of an air-conditioning and refrigeration apparatus significantly.
In order to solve the above-mentioned problems, the present invention combines the refrigerant cycle in combination to generate power using the thermal energy of the atmosphere, and further uses the combined cycle to perform heat exchange and consumes power in the air conditioning and refrigeration equipment. It is a composite air-conditioning refrigeration system that can significantly reduce the amount of water, and is extremely useful as an effective use of new natural energy.

Since the present invention uses thermal energy of the atmosphere, it is a power-saving and combined air-conditioning refrigeration apparatus that can be stably operated for 24 hours all year round, and can be installed everywhere, such as each house, large-scale facility, store, and the like.
In addition, since the exhaust heat emitted by the condenser is extremely small, it is very effective for the countermeasure against the heat island phenomenon.

Hereinafter, the composite air-conditioning refrigerating apparatus according to the present invention will be described with reference to the entire configuration diagram shown in FIGS. 1, 2, 3, and 4.

In FIG. 1, during cooling, the compressor 1 in the first cycle is driven by the external driver 15. The one-cycle refrigerant that has been compressed to a high temperature and high pressure flows into the heat exchanger 3 through the refrigerant pipe 10 via the four-way valve 18, and the second-cycle refrigerant sent by the second-cycle circulation pump 6. The heat exchange is performed, the temperature becomes low, and the refrigerant is discharged and enters the expansion valve 2 or the expander 19 shown in FIG.

In FIG. 1, it expands with the expansion valve 2 of a 1st cycle, or drives the generator 17 with the expander 19 of FIG. 2, and it produces electric power.

In FIG. 1, the refrigerant in the first cycle, which has been expanded by the expansion valve 2 or the expander 19 in FIG. 2 and has become low temperature and low pressure, passes through the refrigerant pipe 8 and enters the indoor heat exchanger 5 by the four-way valve 18 for cooling. The heat exchanger 4 exchanges heat with the refrigerant having a high temperature in the second cycle through the four-way valve 18 to increase the temperature, and the refrigerant returns to the compressor 1 through the refrigerant pipe 9 through the four-way valve 18. With this temperature rise of the refrigerant, the driving force required for the compression of the compressor 1 in the first cycle is greatly reduced.

According to FIG. 1, the refrigerant in the second cycle, which has been heated through the heat exchanger 3, enters the heat exchanger 4 through the refrigerant pipe 13 via the four-way valve 18 through the refrigerant pipe 13.

In FIG. 1, the refrigerant of the second cycle passes through the expansion valve 2 of the first cycle or the expander 19 of FIG. 2 and the indoor heat exchanger 5 to raise the temperature of the refrigerant that has become low pressure and low temperature, and refrigerant piping 11 to return to the circulation pump 6.

In FIG. 1, the second cycle refrigerant sent by the circulation pump 6 flows into the heat exchanger 3 through the refrigerant pipe 12 and is heated by heat exchange with the refrigerant having reached the high temperature in the first cycle. Return from 13 to the four-way valve 18.

In FIG. 3, during heating, the compressor 1 in the first cycle is driven by the external driver 15. The refrigerant of the first cycle, which has been compressed and becomes high temperature and high pressure, flows into the indoor heat exchanger 5 from the four-way valve 18 through the refrigerant pipe 9 via the four-way valve 18, performs heating, and exchanges heat through the four-way valve 18. The temperature of the low-temperature refrigerant in the second cycle is raised by the vessel 4 and enters the expansion valve 2 or the expander 19 of FIG. 4 through the refrigerant pipe 8 via the four-way valve 18.

In FIG. 3, the refrigerant that is expanded by the expansion valve 2 in the first cycle or that flows into the expander 19 in FIG. 4 expands to generate the driving force of the expander 19 and drive the generator 17 in FIG. Generate electricity.

In FIG. 3, the refrigerant of the first cycle, which has been expanded by the expansion valve 2 or the expander 19 of FIG. 4 to become low temperature and low pressure, enters the heat exchanger 3 and exchanges heat with the refrigerant having a high temperature in the second cycle. The temperature is raised, and the refrigerant returns to the compressor 1 through the refrigerant pipe 10 and the four-way valve 18. With this temperature rise of the refrigerant, the driving force required for the compression of the compressor 1 in the first cycle is greatly reduced.

In FIG. 3, it is compressed by the compressor 1 of the first cycle, becomes high temperature, flows into the indoor heat exchanger 5 via the four-way valve 18 through the refrigerant pipe 9, and is heated by the refrigerant of the first cycle that is heated. The refrigerant of the second cycle whose temperature has been increased through 4 enters the four-way valve 18 through the refrigerant pipe 14.

In FIG. 3, the second cycle refrigerant having a high temperature enters the heat exchanger 3 through the refrigerant pipe 13 via the four-way valve 18 and passes through the first cycle expansion valve 2 or the expander 19 in FIG. The temperature of the first cycle refrigerant, which has become low pressure and low temperature, is raised, and returns to the circulation pump 6 via the refrigerant pipe 12.

In FIG. 3, the second cycle refrigerant sent by the circulation pump 6 flows into the heat exchanger 4 through the refrigerant pipe 11, is heated by the high-temperature refrigerant in the first cycle, and passes through the refrigerant pipe 14 for the second cycle. The four-way valve 18 is returned.

Hereinafter, another combined air-conditioning refrigeration apparatus according to the present invention will be described based on the entire configuration diagram shown in FIGS. 5, 6, 7, and 8.

In FIG. 5, during cooling, the compressor 1 in the first cycle is driven by the external driver 15. The compressed one-cycle refrigerant that has become high temperature and high pressure flows into the heat exchanger 3 via the four-way valve 18 through the refrigerant pipe 10, and the second-cycle refrigerant and heat sent by the second-cycle refrigerant pump 6. It is exchanged, discharged at a low temperature, passes through the refrigerant pipe 7 and enters the expansion valve 2 or the expander 19 shown in FIG.

In FIG. 5, the refrigerant that is expanded by the expansion valve 2 in the first cycle or that flows into the expander 19 in FIG. 6 expands, generates a driving force for the expander 19, and drives the generator 17 in FIG. Generate electricity.

In FIG. 5, the refrigerant in the first cycle, which is expanded by the expansion valve 2 in FIG. 5 or the expander 19 in FIG. 6 and becomes low temperature and low pressure, enters the indoor heat exchanger 5 by the four-way valve 18, and after cooling, the four-way valve The heat exchanger 4 enters the heat exchanger 4 through 18, heats up with the refrigerant having a high temperature in the second cycle, rises in temperature, and returns to the compressor 1 through the refrigerant pipe 9. With this temperature rise of the refrigerant, the driving force required for the compression of the compressor 1 in the first cycle is greatly reduced.

In FIG. 5, the refrigerant in the second cycle passes through the expansion valve 2 in the first cycle or the expander 19 in FIG. 2 and the indoor heat exchanger 5, and the refrigerant that has become low pressure and low temperature is raised by the heat exchanger 4. It warms and returns to the circulation pump 6 through the refrigerant | coolant piping 11. FIG.

In FIG. 5, the second cycle refrigerant sent by the circulation pump 6 flows into the heat exchanger 3 through the refrigerant pipe 12 and is heated by heat exchange with the refrigerant having reached the high temperature in the first cycle. Return from 13 to the heat exchanger 4.

In FIG. 7, during heating, the compressor 1 in the first cycle is driven by the external driver 15. The refrigerant of the first cycle, which has been compressed and becomes high temperature and high pressure, flows into the indoor heat exchanger 5 from the four-way valve 18 through the refrigerant pipe 10, performs heating, and is heated by the heat exchanger 3 through the four-way valve 18. The temperature of the low-temperature refrigerant of two cycles is increased, and the refrigerant enters the expansion valve 2 or the expander 19 shown in FIG.

In FIG. 7, the refrigerant that is expanded by the expansion valve 2 in the first cycle or that flows into the expander 19 of FIG. 8 expands, generates a driving force of the expander 19, and drives the generator 17 of FIG. 8. Generate electricity.

In FIG. 7, the refrigerant of the first cycle, which is expanded by the expansion valve 2 or the expander 19 of FIG. 8 and becomes low temperature and low pressure, enters the heat exchanger 4 and exchanges heat with the refrigerant having a high temperature of the second cycle. The temperature is raised and the refrigerant pipe 9 is returned to the compressor 1. With this temperature rise of the refrigerant, the driving force required for the compression of the compressor 1 in the first cycle is greatly reduced.

In FIG. 7, the refrigerant of the second cycle passes through the indoor heat exchanger 5, the heat exchanger 3, and the expansion valve 2 of the first cycle, or the expander 19 of FIG. Is heated by the heat exchanger 4 and returns to the circulation pump 6 through the refrigerant pipe 11.

In FIG. 7, the second cycle refrigerant sent by the circulation pump 6 flows into the heat exchanger 3 through the refrigerant pipe 12, and is heated by heat exchange with the refrigerant having a high temperature in the first cycle. Return from 13 to the heat exchanger 4.

Hereinafter, the composite air-conditioning refrigeration apparatus for controlling the circulation amount of the refrigerant in the second cycle according to the present invention will be described based on the overall configuration diagram shown in FIG.

In FIG. 9, the second cycle refrigerant sent by the circulation pump 6 flows into the heat exchanger 3 through the refrigerant pipe 12 and is heated by heat exchange with the refrigerant having reached the high temperature in the first cycle. 13 flows into the heat exchanger 4 and circulates through the heat exchanger 3 by the circulation pump 6.
The temperature of the second cycle refrigerant is detected by the temperature sensor 26, and the circulation amount of the circulation pump 6 is controlled by the control device 25, so that the second cycle refrigerant is maintained at an appropriate temperature.

Hereinafter, a two-stage compression composite refrigeration apparatus according to the present invention will be described with reference to an overall configuration diagram shown in FIG.

In FIG. 10, the first stage low-stage compressor 20 is driven by a low-stage compression driver 23. The refrigerant of the first cycle, which has been compressed and heated to the intermediate pressure, flows into the intermediate cooler 27 through the refrigerant pipe 10, bypasses the high-pressure refrigerant of the first cycle, and is expanded by the expansion valve 21 for the intermediate cooler. The heat exchange with the low-temperature and intermediate-pressure refrigerant is performed, and the high-stage compressor 16 is entered.

In FIG. 10, the first stage high stage compressor 16 is driven by a high stage compression drive 24. The compressed one-cycle refrigerant that has become high-temperature and high-pressure flows into the heat exchanger 3, exchanges heat with the refrigerant sent by the second-cycle refrigerant pump 6, is discharged at a low temperature, It enters the expansion valve 2 through the intermediate cooler 27 and the refrigerant pipe 7.

In FIG. 10, the refrigerant in the first cycle, which has been expanded by the expansion valve 2 to become low temperature and low pressure, enters the indoor heat exchanger 5, cools, enters the heat exchanger 4 through the refrigerant pipe 8, and enters the second heat exchanger 4. The temperature is raised by exchanging heat with a refrigerant having a high cycle temperature, and the refrigerant returns to the low-stage compressor 20 through the refrigerant pipe 9. With the temperature rise of the refrigerant, the driving force required for compression of the first stage low-stage compressor 20 is greatly reduced.

In FIG. 10, the second-cycle refrigerant heated by the first-cycle refrigerant compressed by the low-stage compressor 20 and the high-stage compressor 16 and having a high temperature through the heat exchanger 3 is a refrigerant. It enters the heat exchanger 4 through the pipe 13.

In FIG. 10, the refrigerant in the second cycle that has entered the heat exchanger 4 is expanded by the expansion valve 2 in the first cycle to become a low pressure, and exchanges heat with the first cycle refrigerant that has entered the indoor heat exchanger 5 and has been cooled. And enters the refrigerant pump 6 through the refrigerant pipe 11.

In FIG. 10, the second cycle refrigerant sent by the refrigerant pump 6 returns to the heat exchanger 3 through the refrigerant pipe 12.

Here, a specific operation state of the first cycle of the air-conditioning refrigeration system in the case of a normal refrigeration cycle that is not a combined cycle will be described with reference to a solid Ph (Mollier) diagram in FIG.
Point A in the first cycle of the reverse Carnot cycle indicates the state of the refrigerant supplied to the compressor 1 (for example, pressure 0.498 MPa, 5 ° C.), compressed by the compressor 1 driven by the drive 15, At point B (for example, pressure 1.73 MPa, 70 ° C.). A state change from point A to point B is an isentropic change. Point C shows the state of the refrigerant flowing out of the indoor heat exchanger 5 (for example, pressure 1.73 MPa, 34 ° C.). Point D shows the state of the refrigerant at the inlet of the heat exchanger 4 after being expanded by the first cycle expansion valve 2 (for example, pressure 0.498 MPa, 0 ° C.). The state change from the point C to the point D is a geometric enthalpy change. The refrigerant in the first cycle returns from the state at point D to the state at point A via the heat exchanger 4.

Here, a specific operation state of the first cycle during cooling of the combined air-conditioning refrigeration apparatus of the combined cycle will be described with reference to a dashed-dotted line Ph (Mollier) diagram in FIG.
Point E ′ in the first cycle of the reverse Carnot cycle indicates the state of the refrigerant supplied to the compressor 1 (for example, pressure 0.498 MPa, 5 ° C.), and is compressed by the compressor 1 driven by the drive unit 15. The pressure becomes high and high, and at point F ′ (for example, pressure 1.192 MPa, 50 ° C.). The state change from the point E ′ to the point F ′ is an isentropic change. Point G ′ indicates the state of the refrigerant flowing out of the heat exchanger 3 (for example, pressure 1.192 MPa, 20 ° C.). Point H ′ indicates the state of the refrigerant at the inlet of the indoor heat exchanger 5 after being expanded by the first cycle expansion valve 2 (for example, pressure 0.498 MPa, 0 ° C.). The state change from the point G ′ to the point H ′ is a geometric enthalpy change. The refrigerant of the first cycle returns from the state of point H ′ to the state of point A after the temperature of the refrigerant of the second cycle is lowered by heat exchange with the refrigerant of the second cycle in the heat exchanger 4. .

Here, a specific operation state of the first cycle during heating of the combined air-conditioning refrigeration apparatus of the combined cycle will be described with reference to a dashed-dotted line Ph (Mollier) diagram in FIG.
Point A ′ in the first cycle of the reverse Carnot cycle indicates the state of the refrigerant supplied to the compressor 1 (for example, pressure 0.786 MPa, 20 ° C.) and is compressed by the compressor 1 driven by the drive unit 15. The pressure becomes high and high, and at point B ′ (for example, pressure 1.73 MPa, 62 ° C.). The state change from the point A ′ to the point B ′ is an isentropic change. Point C ′ indicates the state of the refrigerant flowing out of the heat exchanger 3 (for example, pressure 1.73 MPa, 32 ° C.). Point D ′ indicates the state of the refrigerant at the inlet of the indoor heat exchanger 5 after being expanded by the first cycle expansion valve 2 (for example, pressure 0.786 MPa, 15 ° C.). The state change from the point C ′ to the point D ′ is a geometric enthalpy change. The refrigerant in the first cycle returns from the state of point D ′ to the state of point A ′ via the indoor heat exchanger 5.

Here, a comparison between the theoretical compression power Δj of the normal refrigeration cycle and the theoretical compression power Δi of the combined air-conditioning refrigeration apparatus in the case of cooling will be described with reference to the Ph (Mollier) diagram of FIG. In FIG. 11, the value of the specific enthalpy of the theoretical compression power Δj generated from the first cycle of the normal refrigeration cycle (for example, h2−h1 = 33 KJ / Kg). The value of the specific enthalpy of the theoretical compression power Δi generated from the first cycle of the combined air-conditioning refrigeration apparatus is (for example, h2′−h1 ′ = 24 KJ / Kg), and the efficiency is improved by, for example, about 28%.
A comparison between the theoretical compression power Δj ′ of the normal refrigeration cycle and the theoretical compression power Δi ′ of the combined air-conditioning refrigeration apparatus in the case of heating will be described with reference to the Ph (Mollier) diagram of FIG. In FIG. 12, the value of the specific enthalpy of the theoretical compression power Δj ′ generated from the first cycle of the normal refrigeration cycle (for example, h2−h1 = 34 KJ / Kg). The value of the specific enthalpy of the theoretical compression power Δi ′ generated from the first cycle of the combined air-conditioning refrigeration apparatus is (for example, h2′−h1 ′ = 19 KJ / Kg), and the efficiency is improved by, for example, about 45%.

Here, the comparison between the coefficient of performance of the normal refrigeration cycle and the coefficient of performance of the refrigeration cycle of the combined air-conditioning refrigeration system in the case of cooling will be described with reference to the Ph (Mollier) diagram of FIG. In FIG. 11, the coefficient of performance of the refrigeration cycle generated from the first cycle of the normal refrigeration cycle is (for example, h1−h4 / h2−h1≈5.03). The coefficient of performance of the refrigeration cycle generated from the first cycle of the combined air-conditioning refrigeration apparatus is (for example, h1′−h4 ′ / h2′−h1′≈7.71), and the efficiency is improved by, for example, about 35%. .
In the case of heating, the comparison of the coefficient of performance of the normal refrigeration cycle and the coefficient of performance of the refrigeration cycle of the combined air-conditioning refrigeration system will be described with reference to the Ph (Mollier) diagram of FIG. In FIG. 12, the coefficient of performance of the refrigeration cycle generated from the first cycle of the normal refrigeration cycle is (for example, h1−h4 / h2−h1≈4.71). The coefficient of performance of the refrigeration cycle generated from the first cycle of the combined air-conditioning refrigeration system is (for example, h1′−h4 ′ / h2′−h1′≈9.26), and the efficiency is improved by, for example, about 49%. .

Configuration diagram showing cooling of a combined air conditioning refrigeration system The block diagram shown in the case of the cooling of the composite air-conditioning refrigerating device which generates electric power using the driving force of the first cycle expander The block diagram which shows in the case of heating of a compound air-conditioning refrigeration system The block diagram shown in the case of the heating of the composite air-conditioning refrigerating device which generates electric power using the driving force of the expander of the first cycle Configuration diagram showing the cooling of another combined air conditioning refrigeration system The block diagram which shows the case of the cooling of the another compound air-conditioning refrigeration apparatus which produces electric power using the driving force of the expander of the 1st cycle The block diagram which shows in the case of the heating of another compound air-conditioning refrigeration system The block diagram which shows the case of the heating of the another compound air-conditioning refrigeration apparatus which produces electric power using the driving force of the expander of the 1st cycle The block diagram which shows the composite air-conditioning refrigeration apparatus which controls the circulation amount of the refrigerant | coolant of a 2nd cycle Configuration diagram of two-stage combined refrigeration system Ph diagram of the first cycle shown in the case of cooling of a combined air conditioning refrigeration system Ph diagram of the first cycle shown in the case of heating of the combined air-conditioning refrigeration system

DESCRIPTION OF SYMBOLS 1 ... 1st cycle compressor, 2 ... 1st cycle expansion valve, 3 ... Heat exchanger, 4 ... Heat exchanger, 5 ... Indoor heat exchanger, 6 ...・ Circulating pump, 7, 8, 9, 10,... First cycle refrigerant piping, 11, 12, 13, 14,... Second cycle refrigerant piping, 15. -High stage compression drive, 17, ... Generator, 18, ... Four-way valve, 19 ... Expander, 20 ... Low stage compressor, 21, ... Expansion valve for intermediate cooler, 22 ... Liquid receiver, 23 ... Low stage compression drive, 24 ... High stage compression drive, 25 ... Control device, 26 ... Temperature sensor, 27 ... Intermediate cooler,

Claims (7)

In a combined air-conditioning refrigeration system having a combined cycle consisting of a first cycle of a reverse Carnot cycle and a second cycle of a refrigerant cycle, it has conventionally been released into the atmosphere by a condenser only for cooling. By utilizing the heat energy of the first cycle and skillfully exchanging and using the refrigerant of the first cycle and the refrigerant of the second cycle, the entire air-conditioning refrigerating capacity and air-conditioning refrigerating efficiency are improved even in cooling and heating. Combined air conditioning refrigeration system that can do things. Using a combined cycle consisting of the first cycle of the reverse Carnot cycle and the second cycle of the refrigerant cycle, the power is taken out from the expander of the first cycle by the generator and used to greatly reduce power consumption. Combined air conditioning refrigeration equipment. In a combined air-conditioning refrigeration system having a combined cycle composed of a first cycle of a reverse Carnot cycle and a second cycle of a refrigerant cycle, the second cycle refrigerant exchanged heat with the high-temperature refrigerant of the first cycle is used. Thus, the refrigerant that has passed through the first cycle expander and has been depressurized and lowered in temperature can be heated by the heat exchanger, reducing the driving force required for the compressor in the first cycle and improving the efficiency. Combined air conditioning refrigeration equipment. In a combined air-conditioning refrigeration system having a combined cycle consisting of a first cycle of a reverse Carnot cycle and a second cycle of a refrigerant cycle, the refrigerant of the second cycle passes through the expander of the first cycle and is depressurized and cooled. The temperature is lowered by heat exchange with the refrigerant, and the condensation temperature of the refrigerant in the first cycle is lowered by heat exchange with the refrigerant in the first cycle, thereby reducing the driving force necessary for the compressor and improving the efficiency. Combined air conditioning refrigeration system that can do things. Using a combined cycle consisting of the first cycle of the reverse Carnot cycle and the second cycle of the refrigerant cycle, an expander is attached instead of the expansion valve of the first cycle, and power is generated and used by the driving force. In the combined air-conditioning refrigerating apparatus that significantly reduces power consumption, the combined air-conditioning refrigerating apparatus using different refrigerants, water, brine, etc. that match the characteristics of the first-cycle refrigerant and the second-cycle refrigerant. . In a combined air-conditioning refrigeration system having a combined cycle consisting of a first cycle of a reverse Carnot cycle and a second cycle of a refrigerant cycle, it has conventionally been released into the atmosphere by a condenser only for cooling. By using the heat energy of the first cycle, the first cycle refrigerant and the second cycle refrigerant are used by exchanging heat to improve the overall air conditioning refrigerating capacity and air conditioning refrigerating efficiency even in cooling and heating. A composite air-conditioning refrigeration apparatus using a first-cycle refrigerant and a second-cycle refrigerant that use different refrigerants, water, brine, and the like that match the respective characteristics. In a combined air-conditioning refrigeration system having a combined cycle consisting of a first cycle of a reverse Carnot cycle and a second cycle of a refrigerant cycle, the unused air that has been conventionally released to the atmosphere by a condenser only for cooling By utilizing heat energy and exchanging heat between the second cycle refrigerant and the first cycle refrigerant, it is possible to improve the overall air conditioning refrigerating capacity and air conditioning refrigerating efficiency even in cooling and heating. In the air-conditioning refrigeration system, a combined air-conditioning refrigeration system that can always maintain the optimum temperature and circulation rate by detecting and controlling the circulation amount of the refrigerant in the second cycle with a temperature sensor.

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