WO2006028218A1 - 冷凍装置 - Google Patents
冷凍装置 Download PDFInfo
- Publication number
- WO2006028218A1 WO2006028218A1 PCT/JP2005/016643 JP2005016643W WO2006028218A1 WO 2006028218 A1 WO2006028218 A1 WO 2006028218A1 JP 2005016643 W JP2005016643 W JP 2005016643W WO 2006028218 A1 WO2006028218 A1 WO 2006028218A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- compressor
- sucked
- valve
- refrigeration apparatus
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
- F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/17—Control issues by controlling the pressure of the condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
Definitions
- an object of the present invention is to allow the compressor to draw a refrigerant in an appropriate wet state that achieves a coefficient of performance that is at or close to the maximum, thereby achieving energy saving operation. Disclosure of the invention
- the first solution is premised on a refrigeration apparatus including a refrigerant circuit (20) having a compressor (31) and performing a refrigeration cycle. And this solution means that the refrigerant is brought into the operating state at that time.
- ⁇ Let the compressor (31) inhale in the wet condition that achieves the optimum coefficient of performance (COP).
- the refrigerant circulates in the refrigerant circuit (20) to perform the vapor compression refrigeration cycle.
- the dryness (wetness) of the refrigerant is set. Since the refrigerant of the set dryness is sucked into the compressor (31), the operation is surely performed with the highest coefficient of performance.
- the second solution is premised on a refrigeration apparatus including a refrigerant circuit (20) having a compressor (31) and performing a refrigeration cycle.
- the refrigerant is sucked into the compressor (31) in an overheated state during the cooling operation, and the refrigerant is sucked into the compressor (31) in a wet state during the heating operation.
- the refrigerant circulates in the refrigerant circuit (20) to perform the vapor compression refrigeration cycle. Then, the target discharge temperature of the compressor (31) with the optimum coefficient of performance is set according to the operating conditions such as the high and low pressures of the refrigeration cycle and the compression efficiency of the compressor (31). In other words, if the dryness of the refrigerant is low, the discharge temperature of the compressor (31) is low, and conversely, if the dryness of the refrigerant is high, the discharge temperature of the compressor (31) is high. The discharge temperature of the compressor (31) corresponding to the dryness of the refrigerant is determined under the rolling conditions. As shown in Fig. 3 and Fig.
- the compressor (31) since the wet refrigerant is sucked into the compressor (31), the compressor (31) is compared with the case where the superheated refrigerant is sucked. The discharge temperature decreases. Therefore, the motor of the compressor (31) can be prevented from being abnormally heated, and the deterioration of the refrigerating machine oil due to the high temperature is suppressed. As a result, the reliability of the compressor (31) is improved.
- the fourth solution means is that in any one of the first to third solution means, an expansion valve (23) is provided in the refrigerant circuit (20). Then, the present solution adjusts the wet state of the refrigerant sucked in the compressor (31) by adjusting the opening degree of the expansion valve (23).
- the fifth solving means is any one of the first to third solving means, wherein the refrigerant circuit (20) includes an evaporator (22, 24) and a compressor (31).
- a gas-liquid separator (25) is provided between the inlet and the suction side.
- the gas-liquid separator (25) has a flow rate adjusting valve (27) and guides the liquid refrigerant in the gas-liquid separator (25) to the suction side of the compressor (31) (26) With Yes.
- the present invention adjusts the wet state of the suction refrigerant of the compressor (31) by adjusting the flow rate adjusting valve (27).
- the sixth solving means is any one of the first to third solving means, wherein the refrigerant circuit (20) is connected to the compressor (31) by a motor of the compressor (31). An expander (33) mechanically connected via (32) is provided. Further, the refrigerant circuit (20) is provided in the bypass pipe (44) in which a part of the refrigerant directed to the expander (33) flows by bypassing the expander (33), and the bypass pipe (44). And a flow regulating valve (45). Then, the present solution adjusts the wet state of the suction refrigerant of the compressor (31) by adjusting the flow rate adjusting valve (45).
- the opening degree of the flow control valve (45) is increased. That is, the amount of refrigerant flowing by bypassing the expander (33) is increased, and the amount of refrigerant flowing to the evaporator is increased. As a result, the amount of refrigerant that cannot be evaporated in the evaporator increases and the refrigerant in a damp state is sucked into the compressor (31).
- the opening degree of the flow control valve (45) is reduced, that is, the expander ( Reduce the amount of refrigerant flowing to the evaporator by reducing the amount of refrigerant flowing by bypassing 33).
- the amount of refrigerant that cannot be completely evaporated in the evaporator is reduced, and the refrigerant with low wetness is sucked into the compressor (31).
- the opening degree of the flow rate adjustment valve (27) is adjusted on the assumption that the dryness of the refrigerant sucked into the compressor (31) is optimized, so that the expander (33)
- the opening degree of the flow rate adjustment valve (27) is adjusted on the assumption that the dryness of the refrigerant sucked into the compressor (31) is optimized, so that the expander (33)
- the refrigerant flow rate in the compressor (31) and the expander (33) is balanced. Therefore, more efficient operation is performed.
- the seventh solving means is that in any one of the first to third solving means, the refrigerant circuit (20) is configured such that the high pressure of the refrigeration cycle is higher than the critical pressure of the refrigerant. Is configured.
- the refrigerant is compressed to a pressure higher than the critical pressure by the compressor (31). That is, the refrigerant discharged from the compressor (31) is in a supercritical state. As a result, even when the wet refrigerant is sucked into the compressor (31), the liquid cooling medium does not exist at least in the discharge section, and so-called liquid compression is reliably avoided.
- the refrigerant is carbon dioxide.
- a device is provided.
- the coefficient of performance (COP) is improved as compared with the case where the superheated refrigerant is sucked. be able to. Furthermore, if the refrigerant sucked in the compressor (31) is brought into a wet state where the coefficient of performance is the highest, the energy saving of operation can be maximized. Further, since the refrigerant in the wet state is sucked into the compressor (31), the discharge temperature of the compressor (31) can be lowered as compared with the case of sucking in the refrigerant in the overheated state, and the compressor (31) Degradation of refrigerating machine oil due to high temperature can be suppressed. Therefore, improve the reliability of the equipment Can do.
- the refrigerant is sucked into the compressor (31) during the heating operation, at least the heating operation can be performed with an optimum coefficient of performance.
- the refrigerant in each operating condition, is sucked into the compressor (31) in a wet state so that the discharge temperature of the compressor (31) becomes a predetermined temperature at which an optimum coefficient of performance is obtained. Since it is made to enter, it can operate reliably with the optimal coefficient of performance. Also, since the wet state of the refrigerant can be adjusted based on the discharge temperature of the compressor (31), the coefficient of performance of the refrigeration cycle can be easily controlled.
- the refrigerant circuit (20) is configured to perform a supercritical cycle in which the high pressure of the refrigeration cycle is higher than the critical pressure of the refrigerant, the discharge of the compressor (31) The cooling medium is surely overheated. Therefore, even if the refrigerant in the wet state is sucked into the compressor (31), the refrigerant is already overheated at the discharge part of the compressor (31), so liquid compression in the compressor (31) is reliably prevented. can do. As a result, a highly reliable device can be provided.
- FIG. 1 is a refrigerant circuit diagram showing a refrigeration apparatus according to Embodiment 1.
- FIG. 2 is a Mollier diagram showing refrigerant behavior in the refrigerant circuit during heating operation.
- FIG. 3 is a simulation data table showing the relationship between the dryness of the refrigerant and the coefficient of performance during heating operation.
- FIG. 4 is a simulation data graph showing the relationship between the dryness of the refrigerant and the coefficient of performance during heating operation.
- the air conditioner (10) is provided with a refrigerant circuit (20).
- the refrigerant circuit (20) is configured as a closed circuit by connecting a compressor (31), an indoor heat exchanger (22), and the like.
- the refrigerant circuit (20) is filled with carbon dioxide (CO) as a refrigerant, and the refrigerant circulates in the vapor.
- CO carbon dioxide
- the four-way selector valve (21) includes four ports.
- the four-way selector valve (21) has a first port connected to the discharge pipe (3a) of the compressor (31) and a second port connected to the compressor (31) via a gas-liquid separator (25).
- the suction port (3b) has a third port connected to one end of the outdoor heat exchanger (24) and a fourth port connected to one end of the indoor heat exchanger (22) via the connecting pipe (13).
- the other end of the indoor heat exchanger (22) is connected to the other end of the outdoor heat exchanger (24) through a communication pipe (14) and an expansion valve (23).
- This four-way selector valve (21) has a state in which the first port and the third port communicate with each other, and a state in which the second port and the fourth port communicate with each other (state on the broken line side shown in FIG. 1), The first port and the fourth port communicate with each other, and the second port and the third port communicate with each other (solid line side shown in FIG. 1).
- the first port and the fourth port communicate with each other, and the second port and the third port communicate with each other (solid line side shown in FIG. 1).
- the indoor heat exchanger (22) functions as an evaporator and the outdoor heat exchanger (24) functions as a radiator during cooling operation, while the outdoor heat exchanger (24) functions as an evaporator during heating operation.
- the indoor heat exchanger (22) functions as a radiator.
- the air conditioner (10) is connected to the compressor (31) during normal cooling operation.
- a gas refrigerant in a predetermined superheated state is sucked, and a refrigerant having a predetermined dryness (wet state) is sucked into the compressor (31) during normal heating operation. That is, the present invention excludes special operations and conditions such as defrost operation, when the high pressure in the refrigeration cycle becomes abnormally high, or when the discharge temperature of the compressor (31) becomes abnormally high. Speak for normal driving!
- the expansion valve in the cooling operation, is configured so that the refrigerant evaporates in the indoor heat exchanger (22) and becomes a gas refrigerant in a predetermined superheated state (for example, a superheat degree of 0 to 5 ° C).
- the opening of (23) is set.
- the opening degree of the expansion valve (23) is set so that the refrigerant evaporates in the outdoor heat exchanger (24) to a predetermined dryness (for example, 0.83 to 0.89). Is done.
- the predetermined dryness is found by simulation, and the coefficient of performance (COP) of the air conditioner (10) during the heating operation is set to an optimal value.
- COP coefficient of performance
- the dryness of the refrigerant sucked into the compressor (31) peaks at 0.83 to 0.89.
- the coefficient of performance decreases as the temperature decreases from the region and conversely increases, and as the degree of dryness exceeds 1.00 and the degree of superheat increases, the coefficient of performance decreases as well. I understand. From this, at least the dryness is less than 1.00, that is, when the wet refrigerant is sucked into the compressor (31), the coefficient of performance approaches the optimum point.
- the high pressure of the refrigeration cycle was set to lOMPa
- the low pressure was set to 3.5 MPa
- the outlet temperature of the indoor heat exchanger (22) was set to 25 ° C
- the compressor (31) This was performed under the operating conditions in which the compression efficiency was set at 70%.
- the simulation was performed using carbon dioxide (CO 2) as a refrigerant. Therefore, the various types described above
- the optimum dryness according to the operating conditions is set by finding the dryness with the best coefficient of performance while changing the operating conditions.
- an operating condition based on the change is set, and the dryness (wet state) of the refrigerant according to the operating condition may be set.
- the air conditioner (10) is configured to adjust the dryness of the refrigerant mainly by adjusting the evaporation capacity in the outdoor heat exchanger (24) by adjusting the opening degree of the expansion valve (23). Yes. In other words, to increase the dryness of the refrigerant, reduce the opening of the expansion valve (23) and In order to reduce the dryness of the expansion valve, the opening of the expansion valve (23) is increased.
- the dryness of the refrigerant is also adjusted by adjusting the opening of the flow rate adjustment valve (27) of the liquid index pipe (26). That is, the flow rate of the liquid refrigerant led from the gas-liquid separator (25) to the compressor (31) is adjusted by adjusting the opening of the flow rate adjusting valve (27), and the wet state of the refrigerant is adjusted! .
- the dryness of the refrigerant sucked into the compressor (31) is determined based on the discharge temperature of the compressor (31). That is, in the air conditioner (10), the degree of dryness of the refrigerant is adjusted by adjusting the opening degree of the expansion valve (23) and the flow rate adjustment valve (27) so that the discharge temperature of the compressor (31) becomes the target discharge temperature. Configured to adjust.
- the target discharge temperature is set to a temperature at which the coefficient of performance is optimal. This is because when the dryness of the refrigerant sucked into the compressor (31) decreases, the discharge temperature of the compressor (31) also decreases, and conversely, when the dryness of the refrigerant increases, the discharge temperature of the compressor (31) increases.
- the operation can be performed with the optimum performance coefficient obtained in the operation state at that time.
- the four-way selector valve (21) is set to the broken line side shown in FIG.
- the motor (32) is energized in this state, the refrigerant circulates in the refrigerant circuit (20) in the direction indicated by the one-dot chain line shown in FIG. 1, and a vapor compression refrigeration cycle is performed.
- the flow control valve (27) of the liquid injection pipe (26) is set to a fully closed state.
- the refrigerant compressed by the compressor (31) is discharged from the discharge pipe (3a). In this state, the refrigerant pressure is higher than its critical pressure.
- the discharged refrigerant flows through the four-way switching valve (21) to the outdoor heat exchanger (24) and exchanges heat with outdoor air to dissipate heat.
- This outdoor heat exchange The refrigerant that has dissipated heat in the exchanger (24) is depressurized to a predetermined pressure by the expansion valve (23), then evaporates by exchanging heat with indoor air in the indoor heat exchanger (22), and is overheated. It becomes. At that time, the indoor air is cooled.
- the superheated gas refrigerant is sucked into the compressor (31) through the suction pipe (3b) through the four-way switching valve (21), and is compressed and discharged again.
- the four-way selector valve (21) is set to the state on the solid line side shown in FIG.
- the motor (32) is energized in this state
- the refrigerant circulates in the refrigerant circuit (20) in the direction of the solid line shown in FIG. 1, and a vapor compression refrigeration cycle is performed.
- the refrigerant state during the circulation is a cycle of A1 ⁇ B1 ⁇ C ⁇ D, as indicated by a one-dot chain line in FIG.
- the flow rate adjustment valve (27) of the liquid injection pipe (26) is set to a fully closed state. Note that the cycle of A ⁇ B ⁇ C ⁇ D in FIG.
- FIG. 2 shows a conventional refrigeration cycle in which the superheat degree of the refrigerant sucked in the compressor (31) is zero.
- the refrigerant at point B discharged from the compressor dissipates heat at the radiator to become refrigerant at point C, and then is depressurized by the expansion mechanism to become refrigerant at point D, and then evaporates at the evaporator.
- gas refrigerant (point A) with zero superheat is drawn into the compressor.
- the refrigerant compressed by the compressor (31) is discharged from the discharge pipe (3a) (point B1 in FIG. 2).
- the pressure of the refrigerant is higher than its critical pressure.
- This discharged refrigerant flows through the four-way switching valve (21) to the indoor heat exchanger (22), and dissipates heat by exchanging heat with indoor air (point C in FIG. 2).
- the room air is heated.
- the refrigerant radiated by the indoor heat exchanger (22) is depressurized to a predetermined pressure by the expansion valve (23) (point D in FIG. 2), and then exchanges heat with the outdoor air by the outdoor heat exchanger (24). Evaporates (point A1 in Figure 2).
- the evaporated refrigerant has a predetermined dryness (wet state) at which the coefficient of performance is optimum.
- This wet refrigerant passes through the four-way selector valve (21), is sucked into the compressor (31) through the suction pipe (3b), is compressed again, becomes a superheated refrigerant, and is discharged. In this way, during heating operation, operation can be performed with an optimum coefficient of performance, and energy-saving operation can be achieved.
- the high pressure or low pressure of the refrigeration cycle is changed to set new operating conditions, and the compressor (31) according to the operating conditions is set.
- a target discharge temperature is set.
- the discharge temperature of the compressor (31) is the target discharge temperature.
- the degree of opening of the expansion valve (23) is adjusted so as to be equal, or the degree of opening of the flow rate adjusting valve (27) of the liquid injection pipe (26) is adjusted. Thereby, the dryness of the refrigerant sucked into the compressor (31) becomes the optimal dryness, and the operation can be performed with the optimum coefficient of performance corresponding to the operation conditions.
- the refrigerant in the wet state is sucked into the compressor (31) during the normal heating operation, the results are higher than in the case of sucking in the refrigerant in the overheated state.
- the coefficient (COP) can be improved.
- the wet refrigerant having the optimum coefficient of performance according to the operating conditions is sucked into the compressor (31), the operation can be reliably performed with the optimum performance coefficient. As a result, energy saving operation can be further promoted.
- the performance coefficient is optimized under normal operation, which is completely different from, for example, defrosting operation or conventional liquid injection when the discharge temperature of the compressor (31) becomes abnormally high. it can.
- the target discharge temperature of the compressor (31) corresponding to the dryness of the refrigerant with the optimum coefficient of performance is set, and the compressor is set so that the discharge temperature of the compressor (31) becomes the target discharge temperature. Since the dryness (wetness) of the refrigerant in (31) is adjusted, the coefficient of performance is surely optimal. You can drive.
- the degree of dryness of the suction refrigerant in the compressor (31) is adjusted by adjusting the opening degree of the expansion valve (23) or the flow rate adjusting valve (27), the optimum results can be surely and easily obtained. It is possible to operate with a coefficient.
- the outdoor heat exchange (24) force that is an evaporator since the refrigerant flowing out is in a gas-liquid two-phase wet state, the refrigerant oil in the heat exchange is easily removed by the refrigerant. More refrigeration oil is returned to 31), and poor lubrication in the compressor (31) can be suppressed. Therefore, the compressor (31) can be further protected in combination with the effects described above.
- the air conditioner (10) of the present embodiment is replaced with a compressor (31) instead of the embodiment 1 having an expansion valve (23) as an expansion mechanism of the refrigeration cycle.
- An expander (33) mechanically connected via a motor (32) is used.
- the compressor (31), the motor (32), and the expander (33) are housed in a casing to constitute one unit.
- the compressor (31) is composed of a positive displacement compressor such as a rotary compressor or a scroll compressor.
- the expander (33) is composed of a positive displacement expander such as a rotary expander or a scroll expander.
- the expander (33) includes a so-called two-stage expander that includes two cylinders, expands in the former cylinder, and then expands further in the latter cylinder. Yes.
- the expander (33) is configured to recover power. That is, the energy generated by the expansion of the refrigerant in the expander (33) is used as rotational power for driving the compressor (31) to recover the power.
- a bridge circuit (41) is provided between the connecting pipe (14) and the outdoor heat exchanger (24) in the outdoor unit (11).
- This bridge circuit (41) is formed by connecting four check valves (CV1 to CV4) in a bridge shape. Specifically, in this bridge circuit (41), the inflow side of the first check valve (CV1) and the fourth check valve (CV4) is connected to the outflow port (3d) of the expander (33).
- the outflow side of the valve (CV2) and the third check valve (CV3) is the inflow port (3c) of the expander (33), the outflow side of the first check valve (CV1) and the second check valve (CV2 ) Is connected to the other end of the indoor heat exchanger (22) via the connecting pipe (14), while the inflow side of the third check valve (CV3) and the outflow side of the fourth check valve (CV4) are the outdoor heat. Connected to the other end of the cross (24).
- the refrigerant circuit (20) is provided with an injection pipe (42).
- One end of the induction pipe (42) is between the bridge circuit (41) and the inflow port (3c) of the expander (33), and the other end is an intermediate port between the front and rear cylinders of the expander (33). (Not shown) are connected to each other.
- the injection pipe (42) is provided with an injection valve (43).
- This injection valve (43) is an electric valve for adjusting the flow rate of the refrigerant in the injection pipe (42), and constitutes a flow rate adjustment valve.
- the refrigerant circuit (20) is provided with a bypass pipe (44).
- the bypass pipe (44) has one end between the bridge circuit (41) and the inflow port (3c) of the expander (33), and the other end connected to the inflow port (3c) of the expander (33) and the bridge circuit. Connected to (41).
- the bypass pipe (44) is provided with a bypass valve (45).
- the bypass valve (45) is an electric valve for adjusting the refrigerant flow rate in the nopass pipe (44), and constitutes a flow rate adjusting valve. That is, in the bypass pipe (44), when the bypass valve (45) is in an open state, a part of the refrigerant flows from the bridge circuit (41) to the expander (33), bypassing the expander (33). It is structured as follows.
- the compressor (31) sucks the gas refrigerant in a predetermined superheat state during the cooling operation, and the compressor (31) during the heating operation. It is configured to suck a predetermined wet state refrigerant.
- the injection valve (43) is used so that the refrigerant evaporates in the indoor heat exchanger (22) to become a gas refrigerant in a predetermined superheated state (for example, a superheat degree of 0 to 5 ° C). Is set.
- the opening degree of the injection valve (43) is set so that the refrigerant evaporates in the outdoor heat exchange (24) and becomes a refrigerant having a predetermined dryness (for example, 0.71 to 0.77).
- the This predetermined dryness is set to a value that gives the best coefficient of performance, as shown in the lower table of Fig. 3 and the graph of line E in Fig. 4.
- the high pressure of the refrigeration cycle is set to lOMPa
- the low pressure is set to 3.5 MPa
- the outlet temperature of the indoor heat exchanger (22) is set to 25 ° C, This was performed under operating conditions where the compression efficiency of the compressor (31) was set to 70%.
- the air conditioner (10) of the present embodiment is configured to adjust the dryness of the refrigerant mainly by adjusting the opening of the injection valve (43) and the bypass valve (45). Specifically, the opening of only the injection valve (43) is adjusted while the above-mentioned no-pass valve (45) remains fully closed. For example, when the dryness of the refrigerant is increased. To reduce the opening of the indicator valve (43) and reduce the dryness of the refrigerant, increase the opening of the injection valve (43). When the opening of the injection valve (43) is fully opened and the refrigerant flow rate in the injection pipe (42) cannot be increased any further, the opening of the injection valve (43) remains fully open. Then, the opening degree of the binos valve (45) is adjusted. In the air conditioner (10), as in the first embodiment, the degree of dryness of the refrigerant is also adjusted by adjusting the opening of the flow rate adjustment valve (27) of the liquid injection pipe (26). Constructed.
- the four-way switching valve (21) is set to the broken line side shown in FIG.
- the motor (32) is energized in this state, the refrigerant circulates in the refrigerant circuit (20) in the direction indicated by the one-dot chain line shown in FIG. 5, and a vapor compression refrigeration cycle is performed.
- the four-way selector valve (21) is switched to the state on the solid line side shown in FIG.
- the motor (32) is energized in this state
- the refrigerant circulates in the refrigerant circuit (20) in the direction indicated by the solid line in FIG. 5, and a vapor compression refrigeration cycle is performed.
- the refrigerant state during the circulation is a cycle of A2 ⁇ B2 ⁇ C ⁇ D2, as shown by a solid line in FIG.
- the bypass valve ( 45 ) and the flow rate adjustment valve (27) are set to a fully closed state.
- the refrigerant discharged from the compressor (31) radiates heat by indoor heat exchange (22) (point C in FIG. 2).
- a part of this refrigerant flows into the front cylinder of the expander (33) through the inflow port (3c), and the rest is injected. It flows into the intermediate port of the expander (33) through the suction pipe (42).
- the refrigerant expands, and the internal energy is converted into the rotational power of the motor (32) and recovered as the power of the compressor (31) (point D2 in FIG. 2).
- the expanded refrigerant flows out of the outflow port (3d) and flows to the outdoor heat exchanger (24) through the fourth check valve (CV4) of the bridge circuit (41).
- the refrigerant evaporates by exchanging heat with the outdoor air (point A2 in FIG. 2).
- the evaporated refrigerant has a predetermined dryness (wet state) at which the coefficient of performance is optimum.
- the high-pressure pressure or low-pressure pressure of the refrigeration cycle is changed to set new operating conditions, and the compressor (31) according to the operating conditions is set.
- a target discharge temperature is set.
- the opening of the injection valve (43) is adjusted so that the discharge temperature of the compressor (31) becomes the target discharge temperature, and when the opening is fully opened, the opening of the bypass valve (45) is adjusted. Is done.
- the opening degree of the flow rate adjusting valve (27) of the liquid injection pipe (26) is appropriately adjusted.
- the refrigerant sucked into the compressor (31) is dried.
- the degree of dryness becomes the optimum dryness, and the operation can be performed with the optimum coefficient of performance according to the operating conditions.
- the present invention may be configured as follows with respect to the above embodiment.
- liquid injection pipe (26) of the gas-liquid separator (25) may be omitted.
- only the expansion valve (23) and the injection valve (43) may be adjusted to adjust the dryness of the refrigerant!
- both the bypass pipe (44) and the injection pipe (42) are provided.
- the flow rate adjusting valve dries the refrigerant. Adjust the degree ⁇ .
- the air conditioner (10) that can be switched between the cooling operation and the heating operation is configured as the air conditioner (10).
- the present invention provides a heating that has only a heating function. Of course, it may be applied to the device.
- the present invention is useful as a refrigeration apparatus including a refrigerant circuit that performs a vapor compression refrigeration cycle.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/662,206 US20090113907A1 (en) | 2004-09-09 | 2005-09-09 | Refrigeration Apparatus |
AU2005280900A AU2005280900B2 (en) | 2004-09-09 | 2005-09-09 | Refrigeration apparatus |
EP05782353.6A EP1795833A4 (en) | 2004-09-09 | 2005-09-09 | COOLER |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004-262176 | 2004-09-09 | ||
JP2004262176A JP2006078087A (ja) | 2004-09-09 | 2004-09-09 | 冷凍装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006028218A1 true WO2006028218A1 (ja) | 2006-03-16 |
Family
ID=36036500
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/016643 WO2006028218A1 (ja) | 2004-09-09 | 2005-09-09 | 冷凍装置 |
Country Status (7)
Country | Link |
---|---|
US (1) | US20090113907A1 (ja) |
EP (1) | EP1795833A4 (ja) |
JP (1) | JP2006078087A (ja) |
KR (1) | KR20070067121A (ja) |
CN (1) | CN100501270C (ja) |
AU (1) | AU2005280900B2 (ja) |
WO (1) | WO2006028218A1 (ja) |
Cited By (2)
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KR100989460B1 (ko) | 2006-10-30 | 2010-10-22 | 다이킨 고교 가부시키가이샤 | 냉동장치의 열원유닛 및 냉동장치 |
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WO2010084552A2 (en) * | 2009-01-20 | 2010-07-29 | Panasonic Corporation | Refrigeration cycle apparatus |
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IT202100007316A1 (it) * | 2021-03-25 | 2022-09-25 | Ariston S P A | Metodo di gestione di una pompa di calore operante con un fluido operativo a basso impatto ambientale |
JP2022157187A (ja) * | 2021-03-31 | 2022-10-14 | ダイキン工業株式会社 | ヒートポンプ装置 |
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- 2005-09-09 CN CNB2005800301205A patent/CN100501270C/zh active Active
- 2005-09-09 US US11/662,206 patent/US20090113907A1/en not_active Abandoned
- 2005-09-09 EP EP05782353.6A patent/EP1795833A4/en not_active Withdrawn
- 2005-09-09 KR KR1020077007764A patent/KR20070067121A/ko not_active Application Discontinuation
- 2005-09-09 AU AU2005280900A patent/AU2005280900B2/en not_active Ceased
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---|---|---|---|---|
KR100989460B1 (ko) | 2006-10-30 | 2010-10-22 | 다이킨 고교 가부시키가이샤 | 냉동장치의 열원유닛 및 냉동장치 |
WO2021205540A1 (ja) * | 2020-04-07 | 2021-10-14 | 三菱電機株式会社 | 冷凍サイクル装置 |
JPWO2021205540A1 (ja) * | 2020-04-07 | 2021-10-14 | ||
JP7309045B2 (ja) | 2020-04-07 | 2023-07-14 | 三菱電機株式会社 | 冷凍サイクル装置 |
Also Published As
Publication number | Publication date |
---|---|
JP2006078087A (ja) | 2006-03-23 |
AU2005280900A1 (en) | 2006-03-16 |
EP1795833A4 (en) | 2014-12-24 |
CN100501270C (zh) | 2009-06-17 |
EP1795833A1 (en) | 2007-06-13 |
AU2005280900B2 (en) | 2009-03-05 |
US20090113907A1 (en) | 2009-05-07 |
CN101014813A (zh) | 2007-08-08 |
KR20070067121A (ko) | 2007-06-27 |
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