WO2006025397A1 - 冷凍装置 - Google Patents
冷凍装置 Download PDFInfo
- Publication number
- WO2006025397A1 WO2006025397A1 PCT/JP2005/015781 JP2005015781W WO2006025397A1 WO 2006025397 A1 WO2006025397 A1 WO 2006025397A1 JP 2005015781 W JP2005015781 W JP 2005015781W WO 2006025397 A1 WO2006025397 A1 WO 2006025397A1
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- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- compressor
- heat exchanger
- refrigerant circuit
- expander
- 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
- 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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
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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
- F25B41/00—Fluid-circulation arrangements
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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
- 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
- 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
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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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
- F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/14—Power generation using energy from the expansion of the refrigerant
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
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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
- F25B2600/2515—Flow 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
- F25B45/00—Arrangements for charging or discharging refrigerant
Definitions
- the present invention relates to a refrigeration apparatus including a refrigerant circuit to which an expander for power recovery is connected.
- Patent Document 1 and Patent Document 2 a refrigerant circuit to which an expander for power recovery is connected is provided, and a refrigeration cycle is performed by circulating the refrigerant in the refrigerant circuit.
- Refrigeration equipment is known.
- the expander is mechanically connected to the compressor by a shaft or the like.
- the power obtained by the expansion of the refrigerant in the expander is used to drive the compressor, and the coefficient of performance (COP) is improved by reducing the input to the motor that drives the compressor.
- COP coefficient of performance
- a compressor and an expander are connected to a refrigerant circuit that is a closed circuit.
- the mass flow rate of the refrigerant passing through the compressor and the mass flow rate of the refrigerant passing through the expander must always be equal.
- the state of refrigerant that is sucked by the compressor and the state of refrigerant flowing into the expander varies depending on the operating state of the refrigeration apparatus. For this reason, for example, when the rotational speeds of the compressor and the expander cannot be set individually, the balance between the amount of refrigerant passing through the compressor and the amount of refrigerant passing through the expander is lost, and under appropriate conditions. There is a risk that the refrigeration cycle cannot be performed.
- the refrigeration apparatus disclosed in Patent Document 1 is provided with a bypass passage that bypasses the expander. In an operating state where the amount of refrigerant passing through the expander is relatively small, the refrigerant is also introduced into the bypass passage, thereby balancing the amount of refrigerant passing through the compressor and the amount of refrigerant passing through the expander. Yes. Furthermore, in the refrigeration apparatus disclosed in Patent Document 2, an expansion valve is provided in series with the expander. In an operation state in which the amount of refrigerant passing through the expander is relatively excessive, the refrigerant is expanded by both the expander and the expansion valve, so that the amount of refrigerant passing through the compressor and the amount of refrigerant passing through the expander are Is balanced.
- Patent Document 1 JP 2001-116371 A Patent Document 2: Japanese Patent Laid-Open No. 2003-121018
- the refrigerant passing through the expander is changed in state to balance the refrigerant passing through the compressor and the refrigerant passing through the expander. I am letting. For this reason, the power that can be recovered from the refrigerant by the expander decreases, and there is a risk that the improvement of COP will be insufficient. That is, when a part of the refrigerant bypasses the expander, the amount of refrigerant passing through the expander decreases, and the power obtained by the expander decreases. In addition, when the refrigerant is expanded by both the expansion valve and the expander, the pressure difference at the inlet / outlet of the expander decreases, and in this case also, the power obtained by the expander decreases.
- the present invention has been made in view of power, and the object of the present invention is to reduce the amount of power that can be recovered by the expander in a refrigeration apparatus including the expander without reducing the amount of power. In any case, it is possible to balance the amount of refrigerant passing through the compressor and the amount of refrigerant passing through the expander.
- a first invention includes a refrigerant circuit (11) to which an expander (16) for power recovery is connected, and a refrigeration apparatus that performs a refrigeration cycle by circulating refrigerant in the refrigerant circuit (11) Is targeted.
- the refrigerant circuit (11) is arranged in the middle of the refrigerant flow path leading to the expander (16) and the force compressor (15).
- the refrigerant adjustment tank (14) is disposed downstream of the evaporator in the refrigerant flow path from the expander (16) to the compressor (15). It is what is done.
- the refrigerant adjustment tank (14) is disposed upstream of the evaporator in the refrigerant flow path from the expander (16) to the compressor (15). It is what is done.
- the gas refrigerant in the refrigerant adjustment tank (14) is compressed.
- a fifth invention is the above first, second, third or fourth invention, wherein the high pressure of the refrigeration cycle performed by circulating the refrigerant in the refrigerant circuit (11) is higher than the critical pressure of the refrigerant. It will be set to a higher value.
- a sixth invention is the above first, second or third invention, wherein the high pressure of the refrigeration cycle performed by circulating the refrigerant in the refrigerant circuit (11) is higher than the critical pressure of the refrigerant.
- Control means (90) for operating the liquid flow rate adjusting mechanism (32) so that the temperature of the refrigerant set and discharged from the compressor (15) becomes a predetermined control target value is provided.
- the high pressure of the refrigeration cycle in which the refrigerant is circulated in the refrigerant circuit (11) is set to a value that is higher than the critical pressure of the refrigerant.
- An eighth invention is the above first, second or third invention, wherein the high pressure of the refrigeration cycle performed by circulating the refrigerant in the refrigerant circuit (11) is higher than the critical pressure of the refrigerant.
- Control means (90) is provided for operating the liquid flow rate adjusting mechanism (32) so that the high pressure of the refrigeration cycle set in the refrigerant circuit (11) is set to a predetermined control target value.
- the high pressure of the refrigeration cycle in which the refrigerant is circulated in the refrigerant circuit (11) is set to a value higher than the critical pressure of the refrigerant.
- control means (90) is such that the coefficient of performance of the refrigeration cycle performed in the refrigerant circuit (11) is the highest value obtained in the operating state at that time.
- control target value is set based on the operating state of the refrigeration cycle.
- control means (90) obtains the coefficient of performance of the refrigeration cycle performed in the refrigerant circuit (11) based on the operation state at that time.
- the best The control target value is set based on the operating state of the refrigeration cycle so that the value becomes.
- control means (90) has the highest coefficient of performance of the refrigeration cycle performed in the refrigerant circuit (11) that can be obtained in the current operating state.
- control target value is set based on the operating state of the refrigeration cycle.
- the refrigerant circuit (11) is filled with carbon dioxide as a refrigerant.
- the refrigerant circuit (11) is provided with the expander (16).
- the refrigerant discharged by the compressor (15) for example, dissipates heat to the outdoor air, then expands in the expander (16), and then evaporates by absorbing heat from the air force. Later, it is sucked into the compressor (15) and compressed.
- the refrigerant circuit (11) the refrigerant circulates in this way, and a refrigeration cycle is performed.
- the refrigerant circuit (11) is provided with a refrigerant adjustment tank (14).
- the refrigerant adjustment tank (14) is for adjusting the amount of refrigerant circulating in the refrigerant circuit (11) by changing the amount of liquid refrigerant stored therein.
- the liquid refrigerant in the refrigerant adjustment tank (14) can be supplied to the suction side of the compressor (15) through the liquid index passage (31)! / RU
- the refrigerant flow rate in the liquid injection passage (31) is adjusted by operating the liquid flow rate adjusting mechanism (32). For example, if the superheat of the refrigerant sucked into the compressor (15) becomes too high and its density becomes too small, the amount of refrigerant that can pass through the compressor (15) is larger than the amount of refrigerant that can pass through the expander (16). If the pressure is too low, the high pressure of the refrigeration cycle may not be set to an appropriate value.
- the refrigerant adjustment tank (14) is arranged in the refrigerant flow path leading to the evaporator force compressor (15) of the refrigerant circuit (11).
- the refrigerant flowing out of the evaporator once flows into the refrigerant adjustment tank (14).
- the compressor (15) is a refrigerant The saturated gas refrigerant in the adjustment tank (14) is sucked.
- the refrigerant adjustment tank (14) is arranged in the refrigerant flow path from the expander (16) to the evaporator in the refrigerant circuit (11).
- the refrigerant that has flowed out of the expander (16) once flows into the refrigerant adjustment tank (14). Then, the saturated liquid refrigerant in the refrigerant adjustment tank (14) is supplied to the evaporator.
- the gas refrigerant in the refrigerant adjustment tank (14) can be supplied to the suction side of the compressor (15) through the gas injection passage (33).
- the refrigerant flow rate in the gas injection passage (33) is adjusted by operating the gas flow rate adjusting mechanism (34). For example, if the refrigerant sucked into the compressor (15) becomes wet and its density becomes too high, the amount of refrigerant that can pass through the compressor (15) is larger than the amount of refrigerant that can pass through the expander (16). There is a risk that the high pressure of the refrigeration cycle cannot be set to an appropriate value.
- the high pressure of the refrigeration cycle performed in the refrigerant circuit (11) is set to a value higher than the critical pressure of the refrigerant. That is, the refrigerant discharged by the compressor (15) is in a supercritical state.
- the control means (90) for operating the liquid flow rate adjusting mechanism (32) is provided.
- the control means (90) operates the liquid flow rate adjusting mechanism (32) the flow rate of the refrigerant supplied to the suction side of the compressor (15) through the liquid index passage (31) changes.
- the state of the refrigerant sucked in the compressor (15) changes, and the temperature of the refrigerant discharged from the compressor (15) also changes.
- the control means (90) operates the liquid flow rate adjusting mechanism (32) so that the temperature of the refrigerant discharged from the compressor (15) becomes a predetermined control target value. ) Adjust the refrigerant supply amount to the force compressor (15).
- the control means (90) for operating the liquid flow rate adjusting mechanism (32) and the gas flow rate adjusting mechanism (34) is provided.
- the control means (90) operates the liquid flow rate adjusting mechanism (32)
- the flow rate of the refrigerant supplied to the suction side of the compressor (15) through the liquid injection passage (31) changes.
- the control means (90) operates the gas flow rate adjusting mechanism (34)
- the flow rate of the refrigerant supplied to the suction side of the compressor (15) through the passage (33) changes.
- the density of refrigerant sucked in the compressor (15) changes, and the temperature of the refrigerant discharged from the compressor (15) also changes.
- control means (90) operates the liquid flow rate adjusting mechanism (32) so that the temperature of the refrigerant from which the compressor (15) force is also discharged reaches a predetermined control target value, and the liquid index passage (31) Adjust the refrigerant supply amount to the compressor (15), or operate the gas flow control mechanism (34) to adjust the refrigerant supply amount to the gas injection passage (33) force compressor (15) .
- the control means (90) for operating the liquid flow rate adjusting mechanism (32) is provided.
- the control means (90) operates the liquid flow rate adjusting mechanism (32) the flow rate of the refrigerant supplied to the suction side of the liquid injection passage (31) force compressor (15) changes, and the suction of the compressor (15) The state of the refrigerant changes. Since the density of the refrigerant discharged from the compressor (15) changes, the density of the refrigerant flowing into the expander (16) also changes, and the high pressure of the refrigeration cycle changes accordingly.
- control means (90) operates the liquid flow rate adjustment mechanism (32) so that the high pressure of the refrigeration cycle performed in the refrigerant circuit (11) becomes a predetermined control target value, and the liquid index passage (31) cap. In addition, adjust the amount of refrigerant supplied to the compressor (15).
- the control means (90) for operating the liquid flow rate adjusting mechanism (32) and the gas flow rate adjusting mechanism (34) is provided.
- the control means (90) operates the liquid flow rate adjusting mechanism (32)
- the flow rate of the refrigerant supplied to the suction side of the compressor (15) through the liquid injection passage (31) changes.
- the control means (90) operates the gas flow rate adjusting mechanism (34)
- the flow rate of the refrigerant supplied to the suction side of the compressor (15) through the gas index passage (33) changes.
- the liquid flow rate adjusting mechanism (32) and the gas flow rate adjusting mechanism (34) are operated in this way, the state of the refrigerant sucked in the compressor (15) changes.
- the control means (90) operates the liquid flow rate adjustment mechanism (32) so that the high pressure of the refrigeration cycle performed in the refrigerant circuit (11) becomes a predetermined control target value, and the liquid indication passage (31) Adjust the refrigerant supply amount to the compressor (15), or operate the gas flow rate adjusting mechanism (34) to increase the gas intake passage (33) force as well as the refrigerant supply amount to the compressor (15). Adjust.
- the control means (90) sets the control target value based on the operating state of the refrigeration cycle. At that time, the control means (90) determines the value of the control target value so that the high pressure of the refrigeration cycle becomes a value at which the highest COP can be obtained in the current operating state.
- CO carbon dioxide
- the refrigerant circuit (11) is provided with the liquid injection passage (31), and the liquid refrigerant can be supplied to the suction side of the compressor (15) through the liquid injection passage (31). Yes. If no measures are taken, the compressor (15) can be used even in an operating state where the balance between the amount of refrigerant that can pass through the compressor (15) and the amount of refrigerant that can pass through the expander (16) is lost.
- the compressor (15) can be used even in an operating state where the balance between the amount of refrigerant that can pass through the compressor (15) and the amount of refrigerant that can pass through the expander (16) is lost.
- the amount of refrigerant that can pass through is balanced. Therefore, according to the present invention, the amount of power that can be recovered by the expander (16) does not decrease, and the amount of refrigerant that passes through the compressor (15) and the refrigerant that passes through the expander (16) regardless of the operating state. It is possible to balance the amount.
- the gas refrigerant in the refrigerant adjustment tank (14) can be supplied to the suction side of the compressor (15) through the gas injection passage (33). Therefore, according to the present invention, even if an operation state in which the amount of refrigerant that can pass through the compressor (15) is excessive as compared with the amount of refrigerant that can pass through the expander (16) without taking any countermeasures, ⁇ Cushion passage (33) The force is also supplied to the suction side of the compressor (15), thereby reducing the amount of refrigerant that can pass through the compressor (15) and the amount of refrigerant that can pass through the expander (16). It becomes possible to balance.
- the control means (90) sets the control target value so that the highest COP can be obtained in the operating state at that time. Therefore, according to the tenth aspect of the invention, not only the amount of refrigerant that can pass through the compressor (15) and the amount of refrigerant that can pass through the expander (16) are balanced, but also the operating conditions of the refrigeration cycle are optimized. can do.
- ⁇ 1 It is a piping system diagram of a refrigerant circuit in the air conditioner of Embodiment 1.
- ⁇ 3 It is a piping system diagram of a refrigerant circuit in the air conditioner of Embodiment 2.
- ⁇ 4 It is a piping system diagram of a refrigerant circuit in the air conditioner of Embodiment 3.
- FIG. 5 is a piping diagram of a refrigerant circuit in the air conditioner of Embodiment 4.
- ⁇ 6 It is a piping system diagram of a refrigerant circuit in the air conditioner of Modification 1 of Embodiment 4. ⁇ 7] It is a piping system diagram of a refrigerant circuit in the air conditioner of Modification 2 of Embodiment 4. ⁇ 8] It is a piping system diagram of a refrigerant circuit in the air conditioner of Modification 3 of Embodiment 4. ⁇ 9] It is a piping system diagram of a refrigerant circuit in the air conditioner of Embodiment 5.
- FIG. 10 is a piping system diagram of a refrigerant circuit in the air conditioner of Embodiment 6.
- ⁇ 11 It is a piping system diagram of a refrigerant circuit in the air conditioner of Embodiment 7.
- ⁇ 12 It is a piping system diagram of a refrigerant circuit in the air conditioner of Embodiment 8.
- FIG. 14 is a piping diagram of a refrigerant circuit in the air conditioner of Modification 2 of Embodiment 8.
- FIG. 15 is a piping diagram of a refrigerant circuit in the air conditioner of Modification 3 of Embodiment 8.
- FIG. 16 is a piping diagram of a refrigerant circuit in the air conditioner of Modification 4 of Embodiment 8.
- FIG. 17 is a piping system diagram of a refrigerant circuit in the air conditioner of Embodiment 9.
- FIG. 18 is a piping diagram of a refrigerant circuit in the air conditioner according to the tenth embodiment.
- FIG. 19 is a piping system diagram of a refrigerant circuit in an air conditioner according to a modification of the tenth embodiment.
- FIG. 20 is a piping system diagram of a refrigerant circuit in the air conditioner of Embodiment 11.
- Air conditioner (refrigeration equipment)
- Liquid side control valve Liquid flow rate adjusting mechanism
- Embodiment 1 of the present invention will be described.
- the air conditioner (10) of the present embodiment is constituted by the refrigeration apparatus according to the present invention.
- the air conditioner (10) includes a refrigerant circuit (11). This refrigerant circuit
- (11) is a closed circuit filled with carbon dioxide (CO 2) as a refrigerant.
- CO 2 carbon dioxide
- a compressor (15), an expander (16), an outdoor heat exchanger (12), an indoor heat exchanger (13), and a refrigerant adjustment tank (14) are provided.
- the refrigerant circuit (11) is provided with two four-way switching valves (21, 22).
- Each of the compressor (15) and the expander (16) is constituted by a positive displacement fluid machine (such as a oscillating piston rotary fluid machine, a rolling piston rotary fluid machine, or a scroll fluid machine).
- a positive displacement fluid machine such as a oscillating piston rotary fluid machine, a rolling piston rotary fluid machine, or a scroll fluid machine.
- the compressor (15) and the expander (16) are housed in one casing together with the motor (17).
- the compressor (15), the expander (16), and the motor (17) are connected by a single shaft.
- Both the outdoor heat exchange (12) and the indoor heat exchange (13) are configured by fin “and” tube heat exchange that allows the refrigerant to exchange heat with air.
- the refrigerant adjustment tank (14) is a tank formed in a vertically long cylindrical shape.
- the two four-way switching valves (21, 22) each have a powerful port.
- Each four-way switching valve (21, 22) has a first state in which the first port communicates with the third port and a second port communicates with the fourth port (state shown by a solid line in FIG. 1). And the second state (state indicated by the broken line in FIG. 1) where the first port and the fourth port communicate with each other and the second port and the third port communicate with each other! /,
- the compressor (15) has its suction side connected to the second port of the first four-way switching valve (21) and its discharge side connected to the first port of the first four-way switching valve (21).
- the first four-way switching valve (21) has a third port connected to one end of the outdoor heat exchanger (12) and a fourth port connected to one end of the indoor heat exchanger (13).
- the expander (16) has its inflow side connected to the third port of the second four-way switching valve (22) and its outflow side connected to the upper part of the refrigerant adjustment tank (14).
- the lower part of the refrigerant adjustment tank (14) is connected to the fourth port of the second four-way switching valve (22).
- the second four-way switching valve (22) has a first port connected to the other end of the outdoor heat exchanger (12) and a second port connected to the other end of the indoor heat exchanger (13).
- the refrigerant adjustment tank (14) distributes the refrigerant from the expander (16) to the outdoor heat exchanger (12) and the indoor heat exchanger (13) that functions as an evaporator. Placed in the middle of the route!
- the refrigerant circuit (11) includes a liquid injection pipe constituting a liquid injection passage.
- the liquid injection pipe (31) and a gas injection pipe (33) constituting a gas injection passage are provided.
- the liquid injection pipe (31) has one end connected to the bottom of the refrigerant adjustment tank (14) and the other end connected to the suction side of the compressor (15).
- a liquid side control valve (32) as a liquid side flow rate adjustment mechanism is provided in the middle of the liquid injection pipe (31).
- the gas injection pipe (33) has one end connected to the top of the refrigerant adjustment tank (14) and the other end connected to the suction side of the compressor (15).
- a gas side control valve (34) is provided as a gas side flow rate adjusting mechanism.
- Each of the liquid side control valve (32) and the gas side control valve (34) is constituted by an electric valve having a variable opening.
- the air conditioner (10) is provided with a controller (90) as control means.
- the controller (90) is configured to adjust the opening of the liquid side control valve (32) and the gas side control valve (34). Specifically, the controller (90) sets the target value of the refrigerant discharge temperature of the compressor (15) as a control target value so that the measured value of the refrigerant discharge temperature of the compressor (15) becomes the control target value. In addition, the opening degree of the liquid side control valve (32) and the gas side control valve (34) is adjusted. At that time, the controller (90) sets the value of the high pressure of the refrigeration cycle that gives the highest coefficient of performance (COP) of the refrigeration cycle as the control target value in the operating state at that time.
- COP coefficient of performance
- the first four-way switching valve (21) and the second four-way switching valve (22) are set to the first state (the state indicated by the solid line in FIG. 1), and the refrigerant flows into the refrigerant circuit (11) in FIG. Cycles as shown by solid arrows.
- the outdoor heat exchanger (12) serves as a gas cooler
- the indoor heat exchanger (13) serves as an evaporator.
- the supercritical refrigerant discharged by the compressor (15) flows into the outdoor heat exchanger (12), dissipates heat to the outdoor air, and then flows into the expander (16).
- the expander (16) the refrigerant flowing in expands, and the power obtained thereby is transmitted to the compressor (15).
- the gas-liquid two-phase refrigerant from which the expander (16) force has also flowed out flows into the refrigerant adjustment tank (14) and is separated into liquid refrigerant and gas refrigerant.
- the liquid refrigerant flowing out of the refrigerant adjustment tank (14) flows into the indoor heat exchanger (13), absorbs heat from the indoor air, and evaporates.
- indoor heat exchange (13) the indoor air is cooled by the refrigerant.
- the refrigerant evaporated in the indoor heat exchanger (13) is sucked into the compressor (15) and compressed.
- the first four-way switching valve (21) and the second four-way switching valve (22) are set to the second state (the state indicated by the broken line in FIG. 1), and the refrigerant flows into the refrigerant circuit (11) in FIG. Circulate as shown by the dashed arrows.
- the indoor heat exchanger (13) serves as a gas cooler
- the outdoor heat exchanger (12) serves as an evaporator.
- the supercritical refrigerant from which the compressor (15) force is also discharged flows into the indoor heat exchanger (13), dissipates heat to the indoor air, and then flows into the expander (16).
- the indoor heat exchange (13) the indoor air is heated by the refrigerant.
- the expander (16) the refrigerant flowing in expands, and the power obtained thereby is transmitted to the compressor (15).
- the refrigerant in the gas-liquid two-phase state that has flowed out of the expander (16) flows into the refrigerant adjustment tank (14) and is separated into liquid refrigerant and gas refrigerant.
- the refrigerant evaporated in the outdoor heat exchanger (12) is sucked into the compressor (15) and compressed.
- the Mollier diagram (pressure-enthalpy diagram) in Fig. 2 shows that the refrigerant evaporating pressure (that is, the low pressure of the refrigeration cycle) is P and the refrigerant temperature at the gas cooler outlet is T.
- the diagram is shown. It is assumed that the refrigeration cycle with the highest coefficient of performance in this operating state is the refrigeration cycle represented by A—B—C—D. In other words, when the temperature of the refrigerant discharged from the compressor (15) reaches T (that is, when the high pressure of the refrigeration cycle becomes P), it is assumed that the COP of the refrigeration d H cycle is the highest.
- the evaporation pressure of the refrigerant that is, the low pressure of the refrigeration cycle
- the state of the refrigerant sucked into the compressor (15) (specifically If the degree of superheat or wetness) and the refrigerant temperature at the gas cooler outlet are determined, the refrigeration cycle high pressure at which the COP of the refrigeration cycle is maximized can be identified accordingly.
- the state of the refrigerant sucked into the compressor (15) is the state of point A ′.
- the refrigerant in the state of point A ′ has a lower density than the refrigerant in the state of point A.
- the refrigerant that reaches the state of point A ' approaches the state of point A, and its density increases.
- the density of the refrigerant sucked into the compressor (15) increases, the density of the refrigerant flowing into the expander (16) also increases accordingly. For this reason, the point C 'has a higher density on the isotherm of temperature T gc
- the temperature of the refrigerant discharged from the compressor (15) decreases and approaches the temperature T.
- the controller (90) sets the control target value related to the discharge refrigerant temperature of the compressor (15). Specifically, the controller (90) acquires an actual measurement value of the low pressure of the refrigeration cycle and an actual measurement value of the refrigerant temperature at the gas cooler outlet from a sensor or the like. On the other hand, the controller (90) stores in advance the refrigerant temperature discharged from the compressor (15) at which the COP of the refrigeration cycle is maximum as a function of the low pressure of the refrigeration cycle and the refrigerant temperature at the gas cooler outlet.
- the state of the refrigerant sucked in the compressor (15) is determined in advance such that “the degree of superheat is 5 ° C.” or “is saturated”.
- the controller (90) performs an operation by substituting the actually measured value obtained for this stored function, and sets the value obtained thereby as the control target value.
- the controller (90) compares the set control target value with the actually measured value of the refrigerant discharge temperature of the compressor (15), and based on the result, the liquid side control valve (32) and the gas Controls the opening of the side control valve (34).
- the controller (90) reduces the opening of the gas side control valve (34). If the measured value of the refrigerant discharge temperature of the compressor (15) is still higher than the control target value even if the gas side control valve (34) is fully closed, the controller (90) will control the liquid side control valve (32). Increase the opening. Conversely, it is assumed that the measured value of the refrigerant temperature discharged from the compressor (15) is lower than the control target value. At this time, if the liquid control valve (32) is open, the controller (90) reduces the opening of the liquid control valve (32). Even if the liquid side control valve (32) is fully closed, the measured value of the refrigerant discharge temperature of the compressor (15) is still controlled. If it is lower than the standard value, the controller (90) increases the opening of the gas side control valve (34).
- a liquid injection pipe (31) is provided in the refrigerant circuit (11), and the liquid coolant is supplied to the suction side of the compressor (15) through the liquid injection pipe (31). Can be supplied. If no measures are taken, the compressor (15) will not be able to balance the refrigerant amount that can pass through the compressor (15) and the refrigerant amount that can pass through the expander (16). By supplying the liquid refrigerant to the suction side and adjusting the density of the suction refrigerant in the compressor (15), it is possible to balance the two and set the high pressure of the refrigeration cycle to an appropriate value.
- the amount of refrigerant that can pass through the compressor (15) and the expander (while the entire amount of refrigerant that has flowed out of the gas cooler force is introduced into the expander (16) as it is.
- the amount of refrigerant that can pass through 16) can be balanced. Therefore, according to the present embodiment, the amount of power that can be recovered by the expander (16) is not reduced, and the amount of refrigerant that passes through the compressor (15) and the refrigerant that passes through the expander (16) regardless of the operating state. It is possible to balance the amount.
- the gas refrigerant in the refrigerant adjustment tank (14) can be supplied to the suction side of the compressor (15) by the gas injection pipe (33). Therefore, according to the present embodiment, even if an operation state in which the amount of refrigerant that can pass through the compressor (15) is excessive as compared with the amount of refrigerant that can pass through the expander (16) if no measures are taken, the gas injection is performed. Piping (33) Force By supplying gas refrigerant to the suction side of the compressor (15), it is possible to balance the amount of refrigerant that can pass through the compressor (15) and the amount of refrigerant that can pass through the expander (16). It becomes ability.
- Embodiment 2 of the present invention will be described.
- the air conditioner (10) of the present embodiment is obtained by changing the configuration of the refrigerant circuit (11) and the controller (90) in the air conditioner (10) of the above embodiment IV.
- the air conditioner (10) of the present embodiment differences from the first embodiment will be described.
- a bridge circuit (40) is provided instead of the second four-way switching valve (22).
- the bridge circuit (40) has four check valves (41 to 44) is connected in a bridge shape.
- the inflow side of the first check valve (41) and the fourth check valve (44) is on the outflow side of the expander (16), and the second check valve (42) and the third check valve (40) are connected.
- the outflow side of the check valve (43) is on the inflow side of the expander (16)
- the outflow side of the first check valve (41) and the inflow side of the second check valve (42) are on the indoor heat exchanger (13).
- the inflow side of the third check valve (43) and the outflow side of the fourth check valve (44) are connected to the other end of the outdoor heat exchanger (12), respectively.
- the arrangement of the refrigerant adjustment tank (14) is different from that of the first embodiment.
- the refrigerant adjustment tank (14) is connected to the compressor (15) that functions as an evaporator of the outdoor heat exchange m ⁇ (12) and the indoor heat exchange (13). It is placed in the middle of the distribution channel.
- the refrigerant adjustment tank (14) has an upper portion connected to the second port of the first four-way switching valve (21) and a top portion connected to the suction side of the compressor (15).
- the liquid injection pipe (31) and the liquid side control valve (32) are provided, and the gas injection pipe (33) and the gas side control valve ( 3 4) is omitted.
- one end of the liquid instruction pipe (31) is connected to the bottom of the refrigerant adjustment tank (14) and the other end is connected to the suction side of the compressor (15). This point is the same as in the case of the first embodiment.
- the controller (90) of the present embodiment only adjusts the opening of the liquid side control valve (32) with the omission of the gas injection pipe (33) and the gas side control valve (34). It is structured to do. That is, the controller (90) sets the target value of the refrigerant discharge temperature of the compressor (15) as a control target value, and sets the target value of the refrigerant discharge temperature of the compressor (15) to the control target value. Adjust the opening of the side control valve (32).
- the first four-way selector valve (21) is set to the first state (the state indicated by the solid line in FIG. 3), and the refrigerant circulates in the refrigerant circuit (11) as indicated by the solid line arrow in FIG. .
- the outdoor heat exchanger (12) serves as a gas cooler
- the indoor heat exchanger (13) serves as an evaporator.
- the compressor (15) force discharged supercritical refrigerant is used for outdoor heat exchange (12) Into the outdoor air to dissipate heat and then into the expander (16).
- the expander (16) the refrigerant flowing in expands, and the power obtained thereby is transmitted to the compressor (15).
- the refrigerant that has passed through the indoor heat exchanger (13) flows into the refrigerant adjustment tank (14), and the gas refrigerant in the refrigerant adjustment tank (14) is drawn into the compressor (15) and compressed. At this time, since the liquid refrigerant is stored in the refrigerant adjustment tank (14), the gas refrigerant drawn from the refrigerant adjustment tank (14) to the compressor (15) is saturated.
- the first four-way selector valve (21) is set to the second state (the state indicated by the broken line in FIG. 1), and the refrigerant circulates in the refrigerant circuit (11) as indicated by the broken line arrow in FIG. .
- the indoor heat exchanger (13) serves as a gas cooler
- the outdoor heat exchanger (12) serves as an evaporator.
- the supercritical refrigerant from which the compressor (15) force is also discharged flows into the indoor heat exchanger (13), dissipates heat to the indoor air, and then flows into the expander (16).
- the indoor heat exchange (13) the indoor air is heated by the refrigerant.
- the expander (16) the refrigerant flowing in expands, and the power obtained thereby is transmitted to the compressor (15).
- the refrigerant in the gas-liquid two-phase state that has flowed out of the expander (16) flows into the outdoor heat exchanger (12) and absorbs the outdoor aerodynamic force and evaporates.
- the refrigerant that has passed through the outdoor heat exchanger (12) flows into the refrigerant adjustment tank (14), and the gas refrigerant in the refrigerant adjustment tank (14) is drawn into the compressor (15) and compressed. At this time, since the liquid refrigerant is stored in the refrigerant adjustment tank (14), the gas refrigerant drawn from the refrigerant adjustment tank (14) to the compressor (15) is saturated.
- the controller (90) sets a control target value related to the refrigerant temperature discharged from the compressor (15). At that time, the controller (90) sets the control target value in the same manner as in the first embodiment. In other words, the controller (90) performs a calculation based on the measured value of the low pressure of the refrigeration cycle and the measured value of the refrigerant temperature at the outlet of the gas cooler, so that the compressor (15) having the highest COP of the refrigeration cycle. The discharge refrigerant temperature is calculated, and the value is set as the control target value.
- the controller (90) sets the set control target value of the discharge refrigerant temperature of the compressor (15).
- the opening of the liquid side control valve (32) is controlled based on the result of comparison with the actually measured value. That is, the controller (90) increases the opening of the liquid side control valve (32) when the measured value of the refrigerant discharge temperature of the compressor (15) is higher than the control target value, while the compressor (15) If the measured value of the discharged refrigerant temperature is lower than the control target value, the opening of the liquid side control valve (32) is reduced.
- Embodiment 3 of the present invention will be described.
- the air conditioner (10) of the present embodiment is obtained by changing the configuration of the refrigerant circuit (11) in the air conditioner (10) of the second embodiment.
- the air conditioner (10) of the present embodiment differences from the second embodiment will be described.
- an internal heat exchanger (50) is added to the refrigerant circuit (11) of the present embodiment.
- the internal heat exchanger (50) includes a first channel (51) and a second channel (52), and heats the refrigerant in the first channel (51) and the refrigerant in the second channel (52). Let them exchange.
- the heat transfer area facing the second flow path (52) is larger than the heat transfer area facing the first flow path (51).
- the first flow path (51) is connected to the pipe between the bridge circuit (40) and the outdoor heat exchanger (12), and the second flow path (52) is connected to the bridge circuit (40 ) And indoor heat exchange (1 3) connected to the piping!
- the refrigerant circulates in the refrigerant circuit (11) as shown by the solid arrows in FIG.
- the liquid refrigerant flowing out of the outdoor heat exchanger (12) flows through the first flow path (51) and flows out of the expander (16) in a gas-liquid two-phase state.
- the amount of heat exchange between the refrigerant in the first flow path (51) and the refrigerant in the second flow path (52) is relatively large, and the liquid refrigerant flows while passing through the first flow path (51).
- the temperature drops relatively large.
- the refrigerant whose temperature has decreased while passing through the first flow path (51) is then sent to the expander (16). In this way, the refrigerant that has been cooled by the internal heat exchanger (50) and increased in density is introduced into the expander (16).
- the refrigerant circulates in the refrigerant circuit (11) as shown by the dashed arrows in FIG.
- the gas-liquid two-phase refrigerant that has also flowed out of the expander (16) flows through the first flow path (51) and flows out of the indoor heat exchanger (13).
- the second channel ( 52) That is, in the internal heat exchanger (50), the gas-liquid two-phase refrigerant flows through the first flow path (51) having a small heat transfer area.
- the amount of heat exchange between the refrigerant in the first flow path (51) and the refrigerant in the second flow path (52) is relatively small, and the liquid refrigerant flows while passing through the first flow path (51). The temperature does not drop so much.
- the refrigerant that has passed through the first flow path (51) is then sent to the expander (16).
- the expanded refrigerant (16) is introduced with a refrigerant that is not cooled by the internal heat exchange (50) and hardly changes in density.
- Embodiment 4 of the present invention will be described.
- the air conditioner (10) of the present embodiment is obtained by changing the configuration of the refrigerant circuit (11) in the air conditioner (10) of the third embodiment.
- differences from the third embodiment will be described.
- the arrangement of the refrigerant adjustment tank (14) is different from that of the third embodiment.
- the refrigerant adjustment tank (14) is provided in the middle of the refrigerant flow path from the expander (16) to the outdoor heat exchanger (12) and the indoor heat exchanger (13) that functions as an evaporator. It is arranged in
- a fifth check valve (45) and a sixth check valve (46) are added to the refrigerant circuit (11).
- the fifth check valve (45) is provided in a pipe connecting the second flow path (52) of the internal heat exchanger (50) and the indoor heat exchanger (13).
- the fifth check valve (45) is arranged in such a posture that its inflow side is closer to the indoor heat exchange (13) and its outflow side is closer to the internal heat exchange (50).
- the sixth check valve (46) is provided in a pipe connecting the first flow path (51) of the internal heat exchanger (50) and the outdoor heat exchanger (12).
- the sixth check valve (46) is arranged so that its inflow side is close to the outdoor heat exchange (12) and its outflow side is close to the internal heat exchange (50).
- an introduction pipe (60) is added to the refrigerant circuit (11).
- One end of the introduction pipe (60) is connected to the top of the refrigerant adjustment tank (14).
- the other end of the introduction pipe (60) is bifurcated.
- One of the branches is a first introduction branch pipe (61) and the other is a second introduction branch pipe (62).
- the first introduction branch pipe (61) is connected between the fifth check valve (45) and the internal heat exchanger (50).
- the first introduction branch pipe (61) is provided with a first electromagnetic valve (56).
- the second introduction branch pipe (62) is connected between the sixth check valve (46) and the internal heat exchanger (50).
- the second introduction branch pipe (62) is provided with a second electromagnetic valve (57).
- a first outlet pipe (68) and a second outlet pipe (69) are added to the refrigerant circuit (11).
- the first outlet pipe (68) has one end connected to the lower part of the refrigerant adjustment tank (14) and the other end connected between the indoor heat exchanger (13) and the fifth check valve (45).
- the first lead-out pipe (68) is provided with a seventh check valve (47) that allows only one end of the refrigerant to flow toward the other end.
- the second outlet pipe (69) has one end connected to the lower part of the refrigerant adjustment tank (14) and the other end connected between the outdoor heat exchanger (12) and the sixth check valve (46). .
- the second lead-out pipe (69) is provided with an eighth check valve (48) that allows only one refrigerant to flow toward the other end.
- the first solenoid valve (56) is opened and the second solenoid valve (57) is closed.
- the refrigerant circulates as shown by solid line arrows in FIG. Specifically, the refrigerant in the gas-liquid two-phase state that has flowed out of the expander (16) passes through the second flow path (52) of the internal heat exchange (50), and then the first introduction branch pipe (61) Through the refrigerant adjustment tank (14).
- the refrigerant flowing in is separated into liquid refrigerant and gas refrigerant.
- the liquid refrigerant in the refrigerant adjustment tank (14) is sent to the indoor heat exchanger (13) through the first outlet pipe (68).
- the first solenoid valve (56) is closed and the second solenoid valve (57) is opened.
- the refrigerant circulates as shown by the dashed arrows in FIG. Specifically, the gas-liquid two-phase refrigerant from which the force of the expander (16) has also flowed passes through the first flow path (51) of the internal heat exchanger (50) and then the second introduction branch pipe (62). Through the refrigerant adjustment tank (14). In the refrigerant adjustment tank (14), the refrigerant flowing in is separated into liquid refrigerant and gas refrigerant. The liquid refrigerant in the refrigerant adjustment tank (14) is sent to the outdoor heat exchanger (12) through the second outlet pipe (69).
- the refrigerant circuit (11) may be configured as follows.
- a first three-way valve (26) is provided instead of the first electromagnetic valve (56) and the second electromagnetic valve (57). Yes.
- the first three-way valve (26) is provided at the location where the first introduction branch pipe (61) and the second introduction branch pipe (62) merge in the introduction pipe (60)! /,
- the In the first three-way valve (26), the first introduction branch pipe (61) is connected to the second port, and the second introduction branch pipe (62) is connected to the third port.
- a lead-out pipe (65) is provided instead of the first lead-out pipe (68) and the second lead-out pipe (69).
- One end of the outlet pipe (65) is connected to the lower part of the refrigerant adjustment tank (14).
- the other end of the outlet pipe (65) is bifurcated, and one of the branches is the first outlet branch pipe (66) and the other is the second outlet branch pipe (67).
- the first outlet branch pipe (66) is connected between the indoor heat exchanger (13) and the fifth check valve (45).
- the second outlet branch (67) is connected between the outdoor heat exchanger (12) and the sixth check valve (46)!
- the outlet pipe (65) is provided with a second three-way valve (27).
- the second three-way valve (27) is provided at a location where the first outlet branch pipe (66) and the second outlet branch pipe (67) merge.
- the second three-way valve (27) has a first outlet branch pipe (66) connected to its second port and a second outlet branch pipe (67) connected to its third port.
- the first three-way valve (26) and the second three-way valve (27) are both in a state where the first port and the second port communicate with each other (a state indicated by a solid line in FIG. 6). Is set.
- the refrigerant circulates as shown by solid arrows in FIG. Specifically, the refrigerant in the gas-liquid two-phase state that has flowed out of the expander (16) passes through the second flow path (52) of the internal heat exchange (50), and then passes through the first introduction branch pipe (61). And flows into the refrigerant adjustment tank (14). The liquid refrigerant in the refrigerant adjustment tank (14) is sent to the indoor heat exchanger (13) through the first outlet branch pipe (66).
- the first three-way valve (26) and the second three-way valve (27) are both in a state where the first port and the third port are in communication (shown by broken lines in FIG. 6). Status).
- the refrigerant circulates as shown by the dashed arrows in FIG. Specifically, the refrigerant in the gas-liquid two-phase state that has flowed out of the expander (16) passes through the first flow path (51) of the internal heat exchange (50), and then the second introduction branch pipe (62). Through the refrigerant adjustment tank (14).
- the liquid refrigerant in the refrigerant adjustment tank (14) is sent to the outdoor heat exchanger (12) through the second outlet branch pipe (67).
- the refrigerant circuit (11) may be configured as follows. As shown in FIG. 7, in the refrigerant circuit (11) of the present modification, a second four-way switching valve (22) is provided instead of the bridge circuit (40). In the second four-way selector valve (22), the first port is in the first flow path (51) of the internal heat exchanger (50), and the second port is the second flow path in the internal heat exchanger (50) ( 52), the third port is connected to the inflow side of the expander (16), and the fourth port is connected to the outflow side of the expander (16).
- the first and second solenoid valves (56, 57) and the fifth to eighth check valves (45 to 48) are omitted.
- a four-way selector valve (23) and a fourth four-way selector valve (24) are provided.
- the third four-way selector valve (23) has a first port for the first outlet pipe (68), a second port for the second flow path (52) of the internal heat exchanger (50), and a third port. Is connected to the other end of the indoor heat exchanger (13), and the fourth port is connected to the first introduction branch pipe (61).
- the fourth four-way selector valve (24) has a first port at the other end of the outdoor heat exchanger (12), a second port at the second introduction branch pipe (62), and a third port at the internal heat exchanger.
- the fourth port is connected to the first flow path (51) of the turn (50) and the second lead pipe (69).
- the refrigerant circuit (11) may be configured as follows.
- a second circuit is used instead of the bridge circuit (40).
- a four-way switching valve (22) is provided.
- the second four-way selector valve (22) has a first port for the third four-way selector valve (23) described later, and a second port for the second flow path (52) of the internal heat exchange (50).
- the third port is connected to the inflow side of the expander (16), and the fourth port is connected to the outflow side of the expander (16).
- the sixth check valve (46) is omitted, and a third four-way switching valve (23) and a third electromagnetic valve (58) are added instead.
- the third four-way selector valve (23) has a first port at the other end of the outdoor heat exchanger (12), a second port at the first port of the second four-way selector valve (22), and a third port. The port is connected to one end of the first flow path (51) of the internal heat exchanger (50), and the fourth port is connected to the other end of the first flow path (51) of the internal heat exchange (50). .
- the third solenoid valve (58) is disposed between the fourth port of the third four-way switching valve (23) and the first flow path (51) of the internal heat exchanger (50).
- connection positions of the second introduction branch pipe (62) and the second outlet pipe (69) are changed.
- the second introduction branch pipe (62) is connected between the first flow path (51) and the third solenoid valve (58) of the internal heat exchange (50).
- the second outlet pipe (69) is connected between the fourth port of the third four-way switching valve (23) and the third electromagnetic valve (58).
- Embodiment 5 of the present invention will be described.
- the air conditioner (10) of this embodiment is obtained by changing the configuration of the refrigerant circuit (11) in the air conditioner (10) of the above embodiment i.
- the air conditioner (10) of the present embodiment differences from the first embodiment will be described.
- the first four-way selector valve (21) has a first port at the discharge side of the compressor (15), a second port at the lower part of the refrigerant adjustment tank (14), and a third port at the outdoor heat exchanger ( The fourth port is connected to one end of 12) and the other end of the indoor heat exchanger (13).
- the second four-way selector valve (22) has a first port at the other end of the outdoor heat exchange (12), a second port at the one end of the indoor heat exchange (13), and a third port at the expander On the inflow side of (16), the fourth port is connected to the suction side of the compressor (15).
- the liquid injection pipe (31) and the gas injection pipe (33) are both connected between the suction side of the compressor (15) and the second four-way switching valve (22).
- both the first four-way switching valve (21) and the second four-way switching valve (22) are set to the first state (the state indicated by the solid line in FIG. 9).
- the refrigerant circulates as shown by solid line arrows in FIG. That is, the refrigerant discharged from the compressor (15) sequentially passes through the outdoor heat exchanger (12), the expander (16), the refrigerant adjustment tank (14), and the indoor heat exchanger (13), and then compressed. Inhaled into the machine (15) and compressed.
- the first four-way switching valve (21) and the second four-way switching valve (22) are all set to the second state (the state indicated by the broken line in FIG. 9). Then, in the refrigerant circuit (11), the refrigerant circulates as shown by the dashed arrows in FIG. That is, the refrigerant discharged by the compressor (15) force passes through the indoor heat exchanger (13), the expander (16), the refrigerant adjustment tank (14), and the outdoor heat exchanger (12) in this order, and then It is sucked into the compressor (15) and compressed.
- Embodiment 6 of the present invention will be described.
- the air conditioner (10) of the present embodiment is obtained by changing the configuration of the refrigerant circuit (11) in the air conditioner (10) of the fifth embodiment.
- differences from the fifth embodiment will be described.
- the arrangement of the refrigerant adjustment tank (14) is different from that of the fifth embodiment.
- the refrigerant adjustment tank (14) is a refrigerant flow path from the outdoor heat exchanger (12) and the indoor heat exchanger (13) that functions as an evaporator to the compressor (15). It is arranged in the middle.
- the refrigerant adjusting tank (14) has its upper part connected to the fourth port of the second four-way switching valve (22) and its top connected to the suction side of the compressor (15). .
- the second port of the first four-way switching valve (21) is connected to the outflow side of the expander (16).
- the refrigerant circuit (11) of the present embodiment only the liquid injection pipe (31) and the liquid side regulating valve (32) are provided, and the gas injection pipe (33) and the gas side regulating valve ( 3 4) is omitted.
- one end of the liquid instruction pipe (31) is connected to the bottom of the refrigerant adjustment tank (14) and the other end is connected to the suction side of the compressor (15). This is the same as in the case of the fifth embodiment.
- the controller (90) of the present embodiment only adjusts the opening of the liquid side control valve (32) with the omission of the gas injection pipe (33) and the gas side control valve (34). It is structured to do.
- This controller (90) sets the target value of the refrigerant discharge temperature of the compressor (15) as a control target value, and adjusts the liquid side so that the measured value of the refrigerant discharge temperature of the compressor (15) becomes the control target value. Adjust the opening of the valve (32). That is, the controller (90) is configured in the same manner as that of the second embodiment.
- both the first four-way switching valve (21) and the second four-way switching valve (22) are set to the first state (the state indicated by the solid line in FIG. 10).
- the refrigerant circulates as shown by solid line arrows in FIG. That is, the refrigerant discharged from the compressor (15) sequentially passes through the outdoor heat exchanger (12), the expander (16), the indoor heat exchanger (13), and the refrigerant adjustment tank (14), and then It is sucked into the compressor (15) and compressed.
- the first four-way switching valve (21) and the second four-way switching valve (22) are all set to the second state (the state indicated by the broken line in FIG. 10).
- the refrigerant circulates as shown by the dashed arrows in FIG.
- the refrigerant discharged from the compressor (15) sequentially passes through the indoor heat exchanger (13), the expander (16), the outdoor heat exchanger (12), and the refrigerant adjustment tank (14). It is sucked into the compressor (15) and compressed.
- Embodiment 7 of the present invention will be described.
- the air conditioner (10) of the present embodiment is obtained by changing the configuration of the refrigerant circuit (11) in the air conditioner (10) of the fifth embodiment.
- differences from the fifth embodiment will be described.
- an internal heat exchanger (50) is additionally provided in the refrigerant circuit (11) of the present embodiment.
- This internal heat exchange (50) is configured in the same manner as in the third embodiment.
- the first flow path (51) and the second flow path (52) are provided, and the heat transfer area facing the first flow path (51) is the second flow rate. It is larger than the heat transfer area facing the road (52).
- the first flow path (51) is connected between the first port of the second four-way switching valve (22) and the outdoor heat exchanger (12).
- a passage (52) is connected between the second port of the second four-way switching valve (22) and the indoor heat exchange (13).
- both the first four-way switching valve (21) and the second four-way switching valve (22) are set to the first state (the state indicated by the solid line in FIG. 11).
- the refrigerant circulates as shown by solid line arrows in FIG. That is, the refrigerant that has flowed out the outdoor heat exchange (12) functioning as a gas cooler passes through the first flow path (51) of the internal heat exchange (50) and flows into the force expander (16).
- the refrigerant from which the indoor heat exchange (13) force that functions as an evaporator also flows out passes through the second flow path (52) of the internal heat exchange (50) and is sucked into the force compressor (15).
- the first four-way switching valve (21) and the second four-way switching valve (22) are all set to the second state (the state indicated by the broken line in FIG. 11). Then, in the refrigerant circuit (11), the refrigerant circulates as shown by the dashed arrows in FIG. In other words, the refrigerant from which the indoor heat exchanger (13) force that functions as a gas cooler also flows out passes through the second flow path (52) of the internal heat exchanger (50) and then flows into the expander (16). The refrigerant flowing out of the outdoor heat exchanger (12) functioning as an evaporator passes through the first flow path (51) of the internal heat exchanger (50) to the force compressor (15). Inhaled.
- Embodiment 8 of the present invention will be described.
- the air conditioner (10) of the present embodiment is obtained by changing the configurations of the refrigerant circuit (11) and the controller (90) in the air conditioner (10) of the seventh embodiment.
- the air conditioner (10) of the present embodiment differences from the seventh embodiment will be described.
- a first electromagnetic valve (71) and a second electromagnetic valve (72) are added to the refrigerant circuit (11) of the present embodiment.
- the first solenoid valve (71) is disposed between the second flow path (52) of the internal heat exchanger (50) and the indoor heat exchanger (13).
- the second solenoid valve (72) is disposed between the first flow path (51) of the internal heat exchange (50) and the outdoor heat exchange (12).
- the arrangement of the refrigerant adjustment tank (14) is different from that of the seventh embodiment.
- the refrigerant adjustment tank (14) is a refrigerant flow path leading to a direction compressor (15) that functions as an evaporator of the outdoor heat exchange (12) and the indoor heat exchange (13). It is arranged in the middle.
- the outflow side of the expander (16) is connected to the second port of the first four-way switching valve (21) in the refrigerant circuit (11). Is done.
- the refrigerant circuit (11) is additionally provided with a first introduction pipe (63), a second introduction pipe (64), and a lead-out pipe (65).
- first introduction pipe (63) One end of the first introduction pipe (63) is connected to the upper portion of the refrigerant adjustment tank (14), and the other end is connected between the indoor heat exchanger (13) and the first electromagnetic valve (71). Yes.
- the first introduction pipe (63) is provided with a third electromagnetic valve (73).
- the second introduction pipe (64) has one end connected to the upper part of the refrigerant adjustment tank (14) and the other end connected between the outdoor heat exchanger (12) and the second solenoid valve (72). Yes.
- the second introduction pipe (64) is provided with a fourth solenoid valve (74).
- One end of the outlet pipe (65) is connected to the top of the refrigerant adjustment tank (14).
- the other end of the lead pipe (65) is bifurcated.
- One branch is the first lead branch pipe (66) and the other is the second lead branch pipe (67).
- the first outlet branch pipe (66) is connected between the second flow path (52) of the internal heat exchanger (50) and the first electromagnetic valve (71).
- the first lead-out branch pipe (66) is provided with a first check valve (76).
- This first check valve (76) only allows the refrigerant to flow in the direction in which the refrigerant adjusting tank (14) force flows out.
- the second outlet branch pipe (67) Connected between the first flow path (51) and the second solenoid valve (72) of the internal heat exchanger (50).
- the second lead-out branch pipe (67) is provided with a second check valve (77).
- the second check valve (77) only allows the refrigerant to flow in the direction in which the force of the refrigerant adjustment
- the liquid injection pipe (31) and the liquid side regulating valve (32) are provided, and the gas injection pipe (33) and the gas side regulating valve ( 3 4) is omitted.
- one end of the liquid instruction pipe (31) is connected to the bottom of the refrigerant adjustment tank (14) and the other end is connected to the suction side of the compressor (15). This is the same as in the case of the seventh embodiment.
- the controller (90) of the present embodiment only adjusts the opening of the liquid side control valve (32) with the omission of the gas injection pipe (33) and the gas side control valve (34). It is structured to do.
- This controller (90) sets the target value of the refrigerant discharge temperature of the compressor (15) as a control target value, and adjusts the liquid side so that the measured value of the refrigerant discharge temperature of the compressor (15) becomes the control target value. Adjust the opening of the valve (32). That is, the controller (90) is configured in the same manner as that of the second embodiment.
- the second solenoid valve (72) and the third solenoid valve (73) are opened, and the first solenoid valve (71) and the fourth solenoid valve (74) are closed.
- the refrigerant circulates as shown by solid arrows in FIG. Specifically, the refrigerant that has flowed out of the indoor heat exchanger (13) flows into the refrigerant adjustment tank (14) through the first introduction pipe (63).
- the gas refrigerant in the refrigerant adjustment tank (14) flows into the internal heat exchanger (50) through the first outlet branch pipe (66), passes through the second flow path (52), and then enters the compressor (15). Inhaled.
- the second solenoid valve (72) and the third solenoid valve (73) are closed, and the first solenoid valve (71) and the fourth solenoid valve (74) are opened.
- the refrigerant circulates as shown by the dashed arrows in FIG. Specifically, the refrigerant flowing out of the outdoor heat exchange (12) force flows into the refrigerant adjustment tank (14) through the second introduction pipe (64).
- the gas refrigerant in the refrigerant adjustment tank (14) flows into the internal heat exchanger (50) through the second outlet branch pipe (67), and after passing through the first flow path (51), the compressor (15) Inhaled.
- the refrigerant circuit (11) may be configured as follows. As shown in FIG. 13, in the refrigerant circuit (11) of the present modification, the first to fourth solenoid valves (71 to 74) are omitted, and instead the first three-way valve (26) and the second A three-way valve (27) is provided.
- the first three-way valve (26) is provided in the middle of the pipe connecting the indoor heat exchange (13) and the second flow path (52) of the internal heat exchange (50).
- the first three-way valve (26) has a first port connected to the indoor heat exchanger (13) and a third port connected to the second flow path (52) of the internal heat exchanger (50).
- the first introduction pipe (63) is connected to the second port of the first three-way valve (26).
- the second three-way valve (27) is provided in the middle of the pipe connecting the outdoor heat exchange (12) and the first flow path (51) of the internal heat exchange (50).
- the second three-way valve (27) has a first port connected to the outdoor heat exchanger (12) and a second port connected to the first flow path (51) of the internal heat exchanger (50).
- the second introduction pipe (64) is connected to the third port of the second three-way valve (27).
- the first three-way valve (26) and the second three-way valve (27) are both in a state where the first port and the second port communicate with each other (state shown by a solid line in FIG. 13). Is set.
- the refrigerant circulates as shown by solid line arrows in FIG. Specifically, the refrigerant that flows out of the indoor heat exchange (13) force flows into the refrigerant adjustment tank (14) through the first introduction pipe (63).
- the gas refrigerant in the refrigerant adjustment tank (14) flows into the internal heat exchanger (50) through the first outlet branch pipe (66), passes through the second flow path (52), and then enters the compressor (15 ) Is inhaled.
- the first three-way valve (26) and the second three-way valve (27) are both in a state where the first port and the third port communicate (shown by broken lines in FIG. 13). Status). Then, in the refrigerant circuit (11), the refrigerant circulates as shown by the dashed arrows in FIG. Specifically, outdoor heat exchange (12) force The refrigerant that has flowed out flows into the refrigerant adjustment tank (14) through the second introduction pipe (64). The gas refrigerant in the refrigerant adjustment tank (14) flows into the internal heat exchanger (50) through the second outlet branch pipe (67), and after passing through the first flow path (51), the compressor (15) Inhaled.
- the refrigerant circuit (11) may be configured as follows.
- the first to fourth solenoid valves (71 to 74) and the first and second check valves (76, 77) are omitted.
- a third four-way switching valve (23) and a fourth four-way switching valve (24) are provided.
- the third four-way switching valve (23) is provided in the middle of the pipe connecting the indoor heat exchanger (13) and the second flow path (52) of the internal heat exchanger (50).
- the third four-way selector valve (23) has a first port connected to the indoor heat exchanger (13) and a fourth port connected to the second flow path (52) of the internal heat exchanger (50). ing.
- the first port (66) is connected to the second port, and the first inlet pipe (63) is connected to the third port.
- the fourth four-way selector valve (24) is provided in the middle of the pipe connecting the outdoor heat exchanger (12) and the first flow path (51) of the internal heat exchanger (50).
- the fourth four-way selector valve (24) has a first port connected to the outdoor heat exchanger (12) and a third port connected to the first flow path (51) of the internal heat exchanger (50). ing.
- the fourth four-way selector valve (24) has a second outlet branch pipe (67) connected to the second port and a second inlet pipe (64) connected to the fourth port.
- the refrigerant circuit (11) the refrigerant circulates as shown by solid arrows in FIG. Specifically, the refrigerant flowing out of the indoor heat exchanger (13) flows into the refrigerant adjustment tank (14) through the first introduction pipe (63). The gas refrigerant in the refrigerant adjustment tank (14) flows into the internal heat exchanger (50) through the first outlet branch pipe (66), passes through the second flow path (52), and then enters the compressor (15 ) Is inhaled.
- the refrigerant circuit (11) the refrigerant circulates as shown by the dashed arrows in FIG. Specifically, the refrigerant flowing out of the outdoor heat exchanger (12) flows into the refrigerant adjustment tank (14) through the second introduction pipe (64). The gas refrigerant in the refrigerant adjustment tank (14) flows into the internal heat exchanger (50) through the second outlet branch pipe (67), and after passing through the first flow path (51), the compressor ( Inhaled to 15).
- the refrigerant circuit (11) may be configured as follows.
- a third four-way selector valve (23) is added to the refrigerant circuit (11) of the present modification.
- an introduction pipe (60) is provided instead of the first and second introduction pipes (63, 64).
- the third four-way switching valve (23) has an internal force of the outdoor heat exchanger (12). It is arranged in the part that reaches the second four-way switching valve (22) through the first flow path (51) of the partial heat exchanger (50). Specifically, the third four-way switching valve (23) has a first port at the other end of the outdoor heat exchange (12) and a second port at the first port of the second four-way switching valve (22). The third port is at one end of the first flow path (51) of the internal heat exchanger (50), and the fourth port is the first flow path (5 of the internal heat exchanger (50)).
- the second solenoid valve (72) is disposed between the fourth port of the third four-way switching valve (23) and the internal heat exchanger (50).
- the second outlet branch pipe (67) is connected between the first flow path (51) and the second electromagnetic valve (72) of the internal heat exchange (50).
- One end of the introduction pipe (60) is connected to the upper part of the refrigerant adjustment tank (14).
- the other end of the introduction pipe (60) is bifurcated.
- One of the branches is the first introduction branch pipe (61) and the other is the second introduction branch pipe (62).
- the first introduction branch pipe (61) is connected between the indoor heat exchanger (13) and the first electromagnetic valve (71).
- the first introduction branch pipe (61) is provided with a third solenoid valve (73).
- the second introduction branch pipe (62) is connected between the fourth port of the third four-way switching valve (23) and the second electromagnetic valve (72).
- the second introduction branch pipe (62) is provided with a fourth electromagnetic valve (74).
- the refrigerant circuit (11) the refrigerant circulates as shown by solid line arrows in FIG. Specifically, the refrigerant from which the power of the indoor heat exchanger (13) has also flowed out flows into the refrigerant adjustment tank (14) through the first introduction branch pipe (61). The gas refrigerant in the refrigerant adjustment tank (14) flows into the internal heat exchanger (50) through the first outlet branch pipe (66), passes through the second flow path (52), and then passes through the compressor (15 ) Is inhaled.
- the refrigerant circulates as shown by the dashed arrows in FIG. Specifically, the refrigerant that has also flowed out of the outdoor heat exchanger (12) flows into the refrigerant adjustment tank (14) through the second introduction branch pipe (62). The gas refrigerant in the refrigerant adjustment tank (14) passes through the second outlet branch pipe (67) and heats inside. It flows into the exchanger (50), passes through the first flow path (51), and is sucked into the compressor (15).
- the refrigerant circuit (11) may be configured as follows. This modification is obtained by changing the configuration of the internal heat exchanger (50) in the second modification of the present embodiment (see FIG. 14).
- the internal heat exchanger (50) of the present embodiment has a third flow path (53) in addition to the first flow path (51) and the second flow path (52). Is provided.
- the internal heat exchanger (50) exchanges heat between the refrigerant in the first flow path (51) and the refrigerant in the second flow path (52), so that the refrigerant in the first flow path (51) and the third flow path (53) ) Is heat-exchanged.
- the heat transfer area facing the second flow path (52) is larger than the heat transfer area facing the first flow path (51) and the third flow path (53). Yes.
- the first flow path (51) of the internal heat exchanger (50) has one end connected to the third port of the fourth four-way switching valve (24) and the other end connected to the second four-way switching valve (22). Each connected to the first port.
- the second flow path (52) of the internal heat exchanger (50) has one end connected to the fourth port of the second four-way switching valve (22) and the other end connected to the suction side of the compressor (15). It is connected.
- the third flow path (53) of the internal heat exchanger (50) has one end connected to the fourth port of the third four-way selector valve (23) and the other end connected to the second port of the second four-way selector valve (22). Connected to each of the two ports.
- the refrigerant circulates as shown by solid arrows in FIG. Specifically, the refrigerant flowing out of the indoor heat exchanger (13) flows into the refrigerant adjustment tank (14) through the first introduction pipe (63). The gas refrigerant in the refrigerant adjustment tank (14) flows into the internal heat exchanger (50) through the first outlet branch pipe (66) and passes through the third flow path (53).
- the refrigerant that has passed through the third flow path (53) then flows into the second flow path (52) of the internal heat exchanger (50), and after passing through the second flow path (52), the compressor (15) Inhaled.
- the refrigerant from which the outdoor heat exchange (12) force also flows out flows into the first flow path (51) of the internal heat exchange (50), and flows into the expander (16) after passing through the first flow path (51). To do.
- the cooling circuit In the refrigerant circuit (11), the cooling circuit The medium circulates as shown by the dashed arrows in FIG. Specifically, the refrigerant flowing out of the outdoor heat exchanger (12) flows into the refrigerant adjustment tank (14) through the second introduction pipe (64). The gas refrigerant in the refrigerant adjustment tank (14) flows into the internal heat exchanger (50) through the second outlet branch pipe (67) and passes through the first flow path (51).
- the refrigerant that has passed through the first flow path (51) then flows into the second flow path (52) of the internal heat exchanger (50), and after passing through the second flow path (52), the compressor (15) Inhaled.
- the refrigerant from which the indoor heat exchange (13) force also flows out flows into the third flow path (53) of the internal heat exchange (50), and then flows into the expander (16) after passing through the third flow path (53). To do.
- Embodiment 9 of the present invention will be described.
- the air conditioner (10) of this embodiment is obtained by changing the configuration of the refrigerant circuit (11) in the air conditioner (10) of the above embodiment i.
- the air conditioner (10) of the present embodiment differences from the first embodiment will be described.
- the refrigerant circuit (11) of the present embodiment is additionally supplemented with an internal heat exchanger (50).
- the internal heat exchanger (50) includes a first flow path (51) and a second flow path (52).
- the refrigerant in the first flow path (51) and the refrigerant in the second flow path (52) Heat exchange.
- the first flow path (51) of the internal heat exchanger (50) is arranged in the middle of the pipe connecting the second port of the second four-way switching valve (22) and the indoor heat exchanger (13).
- the second flow path (52) of the internal heat exchange (50) is arranged in the middle of the pipe connecting the third port of the second four-way switching valve (22) and the expander (16)! .
- the refrigerant circulates in the refrigerant circuit (11) as shown by solid line arrows in FIG.
- the liquid refrigerant flowing out of the refrigerant adjustment tank (14) flows into the first flow path (51) of the internal heat exchange (50).
- the refrigerant flowing out of the outdoor heat exchanger (12) flows into the second flow path (52) of the internal heat exchanger (50).
- the refrigerant flowing through the second flow path (52) is cooled by the refrigerant flowing through the first flow path (51).
- the refrigerant cooled when passing through the second flow path (52) of the internal heat exchanger (50) is introduced into the expander (16).
- the refrigerant circulates in the refrigerant circuit (11) as indicated by the dashed arrows in FIG.
- the liquid refrigerant flowing out of the refrigerant adjustment tank (14) flows into the outdoor heat exchanger (12) without passing through the internal heat exchanger (50).
- the refrigerant from which the indoor heat exchange (13) force has also flowed passes through the first flow path (51) of the internal heat exchanger (50), and then the internal heat exchanger (50).
- the second flow path (52) heat exchange is hardly performed between the refrigerant in the first flow path (51) and the refrigerant in the second flow path (52).
- the refrigerant that has passed through the second flow path (52) of the internal heat exchanger (50) flows into the expander (16) almost as it is when it flows out of the indoor heat exchanger (13). .
- Embodiment 10 of the present invention will be described.
- the air conditioner (10) of the present embodiment is obtained by changing the configuration of the refrigerant circuit (11) and the controller (90) in the air conditioner (10) of the ninth embodiment.
- the air conditioner (10) of the present embodiment differences from the ninth embodiment will be described.
- the arrangement of the refrigerant adjustment tank (14) is different from that of the ninth embodiment.
- the refrigerant adjustment tank (14) is a refrigerant flow path from the outdoor heat exchanger (12) and the indoor heat exchanger (13) that functions as an evaporator to the compressor (15). Placed in the middle of!
- the outflow side of the expander (16) is connected to the fourth port of the second four-way switching valve (22).
- the arrangement of the internal heat exchanger (50) is different from that of the ninth embodiment.
- the lower part of the refrigerant adjustment tank (14) is connected to the second port of the first four-way switching valve (21).
- the first flow path (51) of the internal heat exchanger (50) has one end connected to the top of the refrigerant adjustment tank (14) and the other end connected to the suction side of the compressor (15).
- the second flow path (52) of the internal heat exchanger (50) is arranged in the middle of the pipe connecting the third port of the second four-way switching valve (22) and the expander (16). This is the same as in the ninth embodiment.
- the refrigerant circuit (11) is provided with a first solenoid valve (81) and a bypass pipe (80).
- the first solenoid valve (81) is disposed between the third port of the second four-way switching valve (22) and the second flow path (52) of the internal heat exchanger (50).
- One end of the no-pass pipe (80) expands between the second four-way switching valve (22) and the first solenoid valve (81) and the other end expands with the second flow path (52) of the internal heat exchange (50).
- the nois pipe (80) is provided with a second solenoid valve (82).
- the liquid injection pipe (31) and the liquid side conditioner Only the valve (32) is provided, and the gas injection pipe (33) and the gas side control valve (34) are omitted.
- one end of the liquid instruction pipe (31) is connected to the bottom of the refrigerant adjustment tank (14) and the other end is connected to the suction side of the compressor (15). This point is the same as in the case of the first embodiment.
- the controller (90) of the present embodiment only adjusts the opening of the liquid side control valve (32) with the omission of the gas injection pipe (33) and the gas side control valve (34). It is structured to do.
- This controller (90) sets the target value of the refrigerant discharge temperature of the compressor (15) as a control target value, and adjusts the liquid side so that the measured value of the refrigerant discharge temperature of the compressor (15) becomes the control target value. Adjust the opening of the valve (32). That is, the controller (90) is configured in the same manner as that of the second embodiment.
- the first solenoid valve (81) is opened and the second solenoid valve (82) is closed.
- the refrigerant circulates as shown by solid line arrows in FIG. Specifically, the refrigerant that has flowed out of the outdoor heat exchanger (12) flows into the second flow path (52) of the internal heat exchanger (50). Further, the gas refrigerant flowing out from the refrigerant adjustment tank (14) flows into the first flow path (51) of the internal heat exchange (50).
- the refrigerant flowing through the second flow path (52) is cooled by the refrigerant flowing through the first flow path (51). Then, the refrigerant cooled when passing through the second flow path (52) of the internal heat exchanger (50) is introduced into the expander (16).
- the first solenoid valve (81) is closed and the second solenoid valve (82) is opened.
- the refrigerant circulates as shown by the dashed arrows in FIG. Specifically, the refrigerant from which the indoor heat exchange (13) force also flows out flows into the bypass pipe (80), and flows into the expander (16) without passing through the internal heat exchanger (50). In other words, the refrigerant flowing into the expander (16) generally remains in the state when it flows out of the indoor heat exchanger (13). Further, the gas refrigerant that has flowed out of the refrigerant adjustment tank (14) passes through the first flow path (51) of the internal heat exchange (50) and is sucked into the compressor (15).
- the refrigerant circuit (11) may be configured as follows.
- the first flow path (51) of the internal heat exchanger (50) has one end at the fourth port of the second four-way selector valve (22) and the other end at the top of the refrigerant adjustment tank (14). Are connected to each.
- the second flow path (52) of the internal heat exchanger (50) is arranged in the middle of the pipe connecting the third port of the second four-way switching valve (22) and the expander (16). It is.
- the first solenoid valve (81) is disposed between the first flow path (51) of the internal heat exchanger (50) and the refrigerant adjustment tank (14). ing.
- the bypass pipe (80) has one end between the first flow path (51) of the internal heat exchange (50) and the second four-way switching valve (22). The other end is connected between the first solenoid valve (81) and the refrigerant adjustment tank (14). The point that the second solenoid valve (82) is provided in the bypass pipe (80) is the same.
- the first solenoid valve (81) is opened and the second solenoid valve (82) is closed.
- the refrigerant circulates as shown by solid line arrows in FIG. Specifically, the refrigerant that has flowed out of the outdoor heat exchanger (12) flows into the second flow path (52) of the internal heat exchanger (50). Further, the refrigerant flowing out from the indoor heat exchange (13) flows into the first flow path (51) of the internal heat exchange (50).
- the refrigerant flowing through the second flow path (52) is cooled by the refrigerant flowing through the first flow path (51). Then, the refrigerant cooled when passing through the second flow path (52) of the internal heat exchanger (50) is introduced into the expander (16).
- the first solenoid valve (81) is closed and the second solenoid valve (82) is opened.
- the refrigerant circulates as shown by the dashed arrows in FIG. Specifically, the refrigerant from which the outdoor heat exchange (12) force also flows out flows into the bypass pipe (80) and is sucked into the compressor (15) without passing through the internal heat exchange (50). Further, the refrigerant flowing out from the indoor heat exchanger (13) flows into the expander (16) after passing through the second flow path (52) of the internal heat exchanger (50). Then, the refrigerant flowing into the expander (16) generally remains in the state when it flows out of the indoor heat exchanger (13).
- Embodiment 11 of the present invention will be described.
- the air conditioner (10) of this embodiment is obtained by changing the configuration of the refrigerant circuit (11) in the air conditioner (10) of the above embodiment i. here, Regarding the air conditioner (10) of the present embodiment, differences from the first embodiment will be described.
- the refrigerant circuit (11) of the present embodiment is provided with a heat exchange section (85).
- the heat exchanging section (85) is provided in the middle of the pipe connecting the first port of the second four-way switching valve (22) and the outdoor heat exchanger (12).
- the heat exchanging section (85) is housed in the refrigerant adjustment tank (14) and is in a state of being immersed in the liquid refrigerant in the refrigerant adjustment tank (14).
- the refrigerant circulates in the refrigerant circuit (11) as shown by solid line arrows in FIG.
- the refrigerant in the gas-liquid two-phase state from which the expander (16) force also flows out flows into the refrigerant adjustment tank (14) and is separated into liquid refrigerant and gas refrigerant, and the liquid refrigerant in the refrigerant adjustment tank (14) Sent to indoor heat exchanger (13).
- the refrigerant from which the outdoor heat exchange (12) force has also flowed out flows into the heat exchange section (85) and is cooled by the liquid refrigerant in the refrigerant adjustment tank (14). The refrigerant cooled in the heat exchange section (85) then flows into the expander (16).
- the refrigerant circulates in the refrigerant circuit (11) as shown by the dashed arrows in FIG.
- the gas-liquid two-phase refrigerant from which the expander (16) force has also flowed out flows into the refrigerant adjustment tank (14) and is separated into liquid refrigerant and gas refrigerant.
- the liquid refrigerant in the refrigerant adjustment tank (14) flows into the outdoor heat exchanger (12) after passing through the heat exchange section (85).
- the refrigerant that has flowed out of the indoor heat exchanger (13) flows into the expander (16).
- the controller (90) is configured to control the opening of the liquid side control valve (32) and the gas side control valve (34) so that the high pressure of the refrigeration cycle becomes a predetermined target value. It may be done.
- the controller (90) sets a control target value related to the high pressure of the refrigeration cycle. Specifically, the controller (90) also acquires the measured value of the low pressure of the refrigeration cycle and the measured value of the refrigerant temperature at the gas cooler outlet, as well as the sensor force. On the other hand, the controller (90) stores in advance the high pressure of the refrigeration cycle at which the COP of the refrigeration cycle is highest as a function of the low pressure of the refrigeration cycle and the refrigerant temperature at the gas cooler outlet. At that time, the state of the refrigerant sucked in the compressor (15) is, for example, “superheat is 5 ° C.”! /, Is “saturated” t As such, it is predetermined. The controller (90) performs calculation by substituting the actually measured value obtained for this stored function, and sets the value obtained thereby as the control target value.
- the controller for controlling the opening of the liquid side control valve (32) and the gas side control valve (34) like the controller (90) of the above-described embodiments 1, 5, 7, 9, 11 is set.
- the control target value is compared with the actual measured value of the high pressure of the refrigeration cycle, and the opening of the liquid side control valve (32) and gas side control valve (34) is adjusted based on the result.
- the controller (90) reduces the opening of the gas side control valve (34). If the measured value of the refrigerant discharge temperature of the compressor (15) is still higher than the control target value even when the gas side control valve (34) is fully closed, the controller (90) will control the liquid side control valve (32). Increase the opening. Conversely, it is assumed that the measured value of the refrigerant temperature discharged from the compressor (15) is higher than the control target value. At this time, if the liquid side control valve (32) is in an open state, the controller (90) reduces the opening of the liquid side control valve (32). If the measured value of the refrigerant discharge temperature of the compressor (15) is still lower than the control target value even after the liquid side control valve (32) is fully closed, the controller (90) opens the gas side control valve (34). Increase the degree.
- the opening of the liquid side control valve (32) is adjusted based on the result of comparison with the measured value of high pressure.
- the controller (90) increases the opening of the liquid side control valve (32).
- the controller (90) increases the opening of the gas side control valve (34).
- the present invention relates to a refrigerant circuit to which an expander (16) for power recovery is connected.
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- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Air Conditioning Control Device (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP05776073A EP1808653A1 (en) | 2004-08-31 | 2005-08-30 | Freezing apparatus |
US11/661,315 US20080098758A1 (en) | 2004-08-31 | 2005-08-30 | Refrigeration Apparatus |
AU2005278483A AU2005278483B2 (en) | 2004-08-31 | 2005-08-30 | Refrigeration apparatus |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004252938A JP4375171B2 (ja) | 2004-08-31 | 2004-08-31 | 冷凍装置 |
JP2004-252938 | 2004-08-31 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006025397A1 true WO2006025397A1 (ja) | 2006-03-09 |
Family
ID=36000047
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/015781 WO2006025397A1 (ja) | 2004-08-31 | 2005-08-30 | 冷凍装置 |
Country Status (7)
Country | Link |
---|---|
US (1) | US20080098758A1 (ja) |
EP (1) | EP1808653A1 (ja) |
JP (1) | JP4375171B2 (ja) |
KR (1) | KR100837498B1 (ja) |
CN (1) | CN100458307C (ja) |
AU (1) | AU2005278483B2 (ja) |
WO (1) | WO2006025397A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1795833A1 (en) * | 2004-09-09 | 2007-06-13 | Daikin Industries, Ltd. | Refrigerating apparatus |
EP2077426A4 (en) * | 2006-10-25 | 2012-03-07 | Panasonic Corp | COOLING CYCLE DEVICE AND LIQUID MACHINE USED THEREFOR |
Families Citing this family (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7730729B2 (en) * | 2005-02-10 | 2010-06-08 | Panasonic Corporation | Refrigerating machine |
US7787730B2 (en) | 2006-03-15 | 2010-08-31 | Sumitomo Electric Industries, Ltd. | Optical fiber and broadband light source |
JP4093275B2 (ja) * | 2006-03-20 | 2008-06-04 | ダイキン工業株式会社 | 空気調和装置 |
JP2008002742A (ja) | 2006-06-21 | 2008-01-10 | Daikin Ind Ltd | 冷凍装置 |
EP2302310A1 (en) * | 2008-06-03 | 2011-03-30 | Panasonic Corporation | Refrigeration cycle device |
FR2967483B1 (fr) * | 2010-11-17 | 2015-08-07 | Valeo Systemes Thermiques | Boucle de climatisation, systeme comprenant une telle boucle et procede de mise en oeuvre d'un tel systeme |
DE102011052776B4 (de) * | 2011-04-27 | 2016-12-29 | Dürr Thermea Gmbh | Überkritische Wärmepumpe |
CN104755858A (zh) * | 2012-10-31 | 2015-07-01 | 松下知识产权经营株式会社 | 制冷装置 |
CN105899884B (zh) * | 2014-03-20 | 2018-12-14 | 三菱电机株式会社 | 热源侧单元以及空调装置 |
JP6320566B2 (ja) * | 2015-01-08 | 2018-05-09 | 三菱電機株式会社 | 空気調和機 |
US10415857B2 (en) * | 2015-05-01 | 2019-09-17 | Mayekawa Mfg. Co., Ltd. | Refrigerator and operation method for refrigerator |
EP3159628A1 (de) * | 2015-10-20 | 2017-04-26 | Ulrich Brunner GmbH | Wärmepumpenkreislauf mit einem verdampfer |
BE1024383B1 (nl) * | 2016-02-23 | 2018-02-12 | Atlas Copco Airpower Naamloze Vennootschap | Gasexpansie-inrichting en werkwijze voor het expanderen van gas |
DE102017101304A1 (de) | 2017-01-24 | 2018-07-26 | Ibw Engineering Gmbh | Wärmeübertragungsanlage |
CN106761988B (zh) * | 2017-01-25 | 2018-04-24 | 东南大学 | 一种单膨胀机实现热能梯级分时有机朗肯循环装置及方法 |
US11022355B2 (en) | 2017-03-24 | 2021-06-01 | Johnson Controls Technology Company | Converging suction line for compressor |
CN110715478A (zh) * | 2019-11-28 | 2020-01-21 | 广东美的制冷设备有限公司 | 压缩空气换热*** |
CN110715479A (zh) * | 2019-11-28 | 2020-01-21 | 广东美的制冷设备有限公司 | 压缩空气换热*** |
CN110715477A (zh) * | 2019-11-28 | 2020-01-21 | 广东美的制冷设备有限公司 | 压缩空气换热*** |
CN112706581B (zh) * | 2021-01-04 | 2022-07-12 | 西安交通大学 | 跨临界二氧化碳电动客车空调***及控制方法 |
CN118140102A (zh) * | 2021-10-28 | 2024-06-04 | 三菱电机株式会社 | 制冷循环装置 |
Citations (4)
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JPS597858A (ja) * | 1982-07-03 | 1984-01-17 | 株式会社東芝 | 冷凍サイクル |
JPH07280363A (ja) * | 1994-04-11 | 1995-10-27 | Mitsubishi Heavy Ind Ltd | 冷凍サイクル |
JPH08313074A (ja) * | 1995-05-24 | 1996-11-29 | Mitsubishi Heavy Ind Ltd | 冷凍装置 |
JP2003121018A (ja) * | 2001-10-09 | 2003-04-23 | Daikin Ind Ltd | 冷凍装置 |
Family Cites Families (13)
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US3934424A (en) * | 1973-12-07 | 1976-01-27 | Enserch Corporation | Refrigerant expander compressor |
JPS59157446A (ja) * | 1983-02-22 | 1984-09-06 | 松下電器産業株式会社 | 冷凍サイクル装置 |
JP2987951B2 (ja) * | 1991-02-12 | 1999-12-06 | ダイキン工業株式会社 | 空気調和装置の運転制御装置 |
JPH05302760A (ja) * | 1992-04-27 | 1993-11-16 | Matsushita Refrig Co Ltd | 冷凍サイクル |
JP3275559B2 (ja) * | 1994-09-20 | 2002-04-15 | 株式会社日立製作所 | 冷凍装置 |
US5735134A (en) * | 1996-05-30 | 1998-04-07 | Massachusetts Institute Of Technology | Set point optimization in vapor compression cycles |
US5711161A (en) * | 1996-06-14 | 1998-01-27 | Thermo King Corporation | Bypass refrigerant temperature control system and method |
JPH11173682A (ja) * | 1997-12-10 | 1999-07-02 | Sanyo Electric Co Ltd | 空気調和装置 |
JP2001141315A (ja) * | 1999-11-10 | 2001-05-25 | Aisin Seiki Co Ltd | 冷凍空調機 |
JP2002228282A (ja) * | 2001-01-29 | 2002-08-14 | Matsushita Electric Ind Co Ltd | 冷凍装置 |
JP3598997B2 (ja) * | 2001-05-31 | 2004-12-08 | ダイキン工業株式会社 | 冷凍装置 |
JP3863480B2 (ja) * | 2002-10-31 | 2006-12-27 | 松下電器産業株式会社 | 冷凍サイクル装置 |
US6898941B2 (en) * | 2003-06-16 | 2005-05-31 | Carrier Corporation | Supercritical pressure regulation of vapor compression system by regulation of expansion machine flowrate |
-
2004
- 2004-08-31 JP JP2004252938A patent/JP4375171B2/ja not_active Expired - Fee Related
-
2005
- 2005-08-30 WO PCT/JP2005/015781 patent/WO2006025397A1/ja active Application Filing
- 2005-08-30 KR KR1020077005797A patent/KR100837498B1/ko not_active IP Right Cessation
- 2005-08-30 AU AU2005278483A patent/AU2005278483B2/en not_active Ceased
- 2005-08-30 EP EP05776073A patent/EP1808653A1/en not_active Withdrawn
- 2005-08-30 US US11/661,315 patent/US20080098758A1/en not_active Abandoned
- 2005-08-30 CN CNB2005800284750A patent/CN100458307C/zh not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS597858A (ja) * | 1982-07-03 | 1984-01-17 | 株式会社東芝 | 冷凍サイクル |
JPH07280363A (ja) * | 1994-04-11 | 1995-10-27 | Mitsubishi Heavy Ind Ltd | 冷凍サイクル |
JPH08313074A (ja) * | 1995-05-24 | 1996-11-29 | Mitsubishi Heavy Ind Ltd | 冷凍装置 |
JP2003121018A (ja) * | 2001-10-09 | 2003-04-23 | Daikin Ind Ltd | 冷凍装置 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1795833A1 (en) * | 2004-09-09 | 2007-06-13 | Daikin Industries, Ltd. | Refrigerating apparatus |
EP1795833A4 (en) * | 2004-09-09 | 2014-12-24 | Daikin Ind Ltd | COOLER |
EP2077426A4 (en) * | 2006-10-25 | 2012-03-07 | Panasonic Corp | COOLING CYCLE DEVICE AND LIQUID MACHINE USED THEREFOR |
Also Published As
Publication number | Publication date |
---|---|
AU2005278483B2 (en) | 2009-01-15 |
AU2005278483A1 (en) | 2006-03-09 |
US20080098758A1 (en) | 2008-05-01 |
CN100458307C (zh) | 2009-02-04 |
EP1808653A1 (en) | 2007-07-18 |
JP4375171B2 (ja) | 2009-12-02 |
KR100837498B1 (ko) | 2008-06-12 |
CN101006310A (zh) | 2007-07-25 |
KR20070046922A (ko) | 2007-05-03 |
JP2006071137A (ja) | 2006-03-16 |
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