WO2006120922A1 - 冷凍サイクル装置 - Google Patents
冷凍サイクル装置 Download PDFInfo
- Publication number
- WO2006120922A1 WO2006120922A1 PCT/JP2006/308875 JP2006308875W WO2006120922A1 WO 2006120922 A1 WO2006120922 A1 WO 2006120922A1 JP 2006308875 W JP2006308875 W JP 2006308875W WO 2006120922 A1 WO2006120922 A1 WO 2006120922A1
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- WO
- WIPO (PCT)
- Prior art keywords
- expander
- compressor
- refrigerant
- refrigeration cycle
- valve
- 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
- 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
- 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
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2400/04—Refrigeration circuit bypassing means
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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
- F25B2400/141—Power generation using energy from the expansion of the refrigerant the extracted power is not recycled back in the refrigerant circuit
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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
- F25B2500/00—Problems to be solved
- F25B2500/27—Problems to be solved characterised by the stop of the refrigeration 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2501—Bypass 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2106—Temperatures of fresh outdoor air
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
Definitions
- the present invention relates to a refrigeration cycle apparatus that effectively recovers energy generated by expansion of a refrigerant.
- FIG. 10 shows a conventional refrigeration cycle apparatus described in Patent Document 1.
- the compressor 1 is driven by driving means (not shown) such as an electric motor or a traveling engine to suck and compress the refrigerant.
- the high-temperature and high-pressure refrigerant discharged from the compressor 1 is cooled by the radiator 2.
- the refrigerant flowing out of the radiator 2 is decompressed and expanded by the expander 3.
- the expander 3 converts the expansion energy of the refrigerant that has flowed into mechanical energy (rotational energy) and supplies the converted mechanical energy (rotational energy) to the generator 4 to generate electric power.
- the refrigerant expanded under reduced pressure in the expander 3 is evaporated and evaporated in the evaporator 5 and then sucked into the compressor 1 again.
- Such a refrigeration cycle apparatus converts expansion energy into mechanical energy, and decompresses the refrigerant while causing the expander 3 to perform expansion work. Therefore, the refrigerant flowing out of the radiator 2 is shown in FIG. Thus, the enthalpy is lowered while changing the phase along the isentropic line ( c ⁇ d). Therefore, as compared with the case of simply adiabatic expansion without causing expansion work when the refrigerant is decompressed (when changing isenthalpy), the refrigerant at the refrigerant inlet side and the refrigerant outlet side of the evaporator 5 is increased by the amount of expansion work Aiexp. Since the specific enthalpy difference can be increased, the refrigeration capacity can be increased.
- the generator 4 can generate electric power of (Aiexp portion X power generation efficiency). And the generated power compressor 1 , The input of electric power necessary for driving the compressor 1 can be reduced, and the coefficient of performance (COP) of the refrigeration cycle can be improved.
- Patent Document 1 Japanese Unexamined Patent Publication No. 2000-329416
- the present invention has been made in view of such problems of the prior art, and reduces the amount of refrigerant flowing into the expander shell when the compressor is stopped, so that the refrigerant can be converted into oil in the expander shell.
- the purpose is to achieve a more stable start-up of the refrigeration cycle system by reducing the amount of dissolved!
- a refrigeration cycle apparatus includes a compressor that compresses a refrigerant, a radiator that dissipates the refrigerant discharged from the compressor, and a refrigerant that uses this radiator force.
- An expander that expands the refrigerant and an evaporator that evaporates the refrigerant of the expander power are serially connected in series.
- a refrigerant flow rate adjusting means for adjusting the amount of refrigerant flowing into the expander, and a controller for controlling the compressor and the refrigerant flow rate adjusting means. When the compressor is stopped, the controller is The refrigerant flow rate adjusting means is controlled to reduce the amount of refrigerant flowing into the expander.
- the amount of refrigerant flowing into the expander when the compressor is stopped is reduced, and the amount of refrigerant dissolved in the oil in the expander is reduced. Stable start-up can be realized.
- FIG. 4 is a configuration diagram of a refrigeration cycle apparatus according to Embodiment 2 of the present invention.
- Figure 10 shows the configuration of a conventional refrigeration cycle system
- FIG. 1 shows a schematic diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
- symbol is attached
- a refrigeration cycle apparatus includes a compressor 1, a radiator 2, an on-off valve 6, an expander 3 that recovers refrigerant expansion energy, and an evaporator. Are connected in series via a pipe, and carbon dioxide is sealed as a refrigerant.
- the refrigeration cycle apparatus also includes a controller 21 that controls the compressor 1 and the opening / closing valve 6, and the opening / closing valve 6 functions as a refrigerant flow rate adjusting unit that adjusts the amount of refrigerant flowing into the expander 3.
- an internal high-pressure type expander is used as the expander 3.
- the expansion energy of the refrigerant is converted into mechanical energy (rotational energy). Electric power is generated by supplying the converted mechanical energy (rotational energy) to the generator 4, and the generated electric power is used as a drive source for the compressor 1.
- the change in the energy state of the refrigerant during normal operation is based on the Mollier diagram shown in FIG. explain.
- the low-temperature and low-pressure refrigerant is compressed by the compressor 1 to become a high-temperature and high-pressure refrigerant, and is discharged from the compressor 1 (a ⁇ b).
- the refrigerant discharged from the compressor 1 exchanges heat with tap water in the radiator 2, heats the tap water to a high temperature of about 80 ° C, and flows into the expander 3 (b ⁇ c;).
- the electric power generated by the generator 4 is used as the compressor 1 Efficiency can be improved because the power input of the compressor 1 can be reduced compared to the refrigeration cycle equipment that uses the expansion valve and the cylindrical tube to perform isentropic expansion. To do.
- the evaporator 5 when used as a cooling source for a household refrigerator, commercial refrigerator, air conditioner, ice maker, vending machine, etc., the electric power generated by the generator 4 is used as a drive source for the compressor 1.
- the power input of the compressor 1 is reduced and the refrigeration effect (evaporator) is reduced. 5), the efficiency of the refrigerant is further improved.
- a stop signal of the refrigeration cycle device is input to the controller 21, and the controller 21 stops the operation of the compressor 1,
- the on-off valve 6 is closed.
- the refrigerant flowing into the expander 3 from the radiator 2 side can be shut off after the operation of the compressor 1 is stopped.
- an internal high-pressure expander as the expander 3
- the amount of refrigerant flowing into the expander 3 from the evaporator 5 side can be reduced.
- high-pressure refrigerant is sucked into the sealed container 31 through the inlet side pipe 30.
- the high-pressure refrigerant flows into the first cylinder 33 through the suction hole 32 and expands in the first cylinder 33.
- the first roller 34 is rotated by the expansion force of the refrigerant.
- the refrigerant expanded in the first cylinder 33 flows into the second cylinder 36 through the communication hole 35, further expands in the second cylinder 36, and the second inlet 37 rotates by the expansion force of the refrigerant.
- the low-pressure refrigerant expanded in the second cylinder 36 is discharged from the outlet side pipe 40 through the discharge hole 38 and the discharge hole 39.
- the sealed container 31 is filled with the high-pressure refrigerant, and the outlet side pipe 40 communicating with the evaporator 5 is substantially the same as the high-pressure refrigerant due to the mechanism of the expander. Because it is in the shut-off state, the amount of refrigerant flowing into the expander 3 can be reduced by closing the on-off valve 6 when the compressor 1 is stopped, resulting in insufficient refrigerant circulation when the refrigeration cycle unit is restarted And damage to the expander sliding surface can be prevented.
- the on-off valve 6 is most preferably a valve that can be quickly closed, such as an electromagnetic valve, but is also effective in a slow-closing type such as an expansion valve.
- the expansion energy of the refrigerant is converted into mechanical energy (rotational energy) by the expander 3, and the converted mechanical energy (rotational energy) is supplied to the generator 4 to generate electric power.
- the same effect can be obtained even when the shafts of the compressor 1 and the expander 3 are directly connected to each other and the expansion energy is directly recovered as mechanical energy (rotational energy).
- Embodiment 1 although carbon dioxide is used as the refrigerant, the same effect can be obtained even when a natural refrigerant other than carbon dioxide (for example, ammonia refrigerant or HC refrigerant) or HFC refrigerant is used. Needless to say, you can get it.
- a natural refrigerant other than carbon dioxide for example, ammonia refrigerant or HC refrigerant
- HFC refrigerant HFC refrigerant
- the internal high pressure type expander is used as the expander 3 to reduce the amount of refrigerant flowing into the expander 3 on the side of the evaporator 5, but it is shown in FIG.
- the on-off valve 15 is further arranged on the low pressure side of the expander 3, that is, between the expander 3 and the evaporator 5, the two on-off valves 6 and 15 before and after the expander 3 are closed when the compressor 1 is stopped. By controlling, the refrigerant flowing into the expander 3 can be completely shut off.
- the inlet side pipe 30 and the first cylinder 33 are directly connected, and the low-pressure refrigerant is discharged into the sealed container 31 from the discharge hole 39.
- 31 is filled with a low-pressure refrigerant, and the inlet-side piping 30 communicating with the radiator 2 is substantially cut off from the low-pressure refrigerant due to the mechanism of the expander. Therefore, the on-off valve 15 is disposed between the expander 3 and the evaporator 5, and the on-off valve 15 is closed when the compressor 1 is stopped, whereby the amount of refrigerant flowing into the expander 3 can be reduced, and the refrigeration cycle. Insufficient refrigerant circulation at the time of restarting the device and damage to the expander sliding surface can be prevented.
- an on-off valve 6 is further provided on the high-pressure side of the expander 3, that is, between the expander 3 and the radiator 2.
- the refrigerant flowing into the expander 3 can be completely shut off by closing the two on-off valves 6 and 15 before and after the expander 3 when the compressor 1 is stopped.
- the stop operation of the compressor 1 has been described as the case where the user selects the stop of the refrigeration cycle apparatus.
- the indoor temperature detector is set to a set temperature. Based on the control rules for compressor 1, such as when compressor 1 is stopped when the above is detected. The same applies when V and the compressor 1 are stopped.
- FIG. 4 shows a schematic diagram of a refrigeration cycle apparatus according to Embodiment 2 of the present invention.
- symbol is attached
- the description of components common to those in Fig. 1 is omitted.
- the radiator 2 that radiates the refrigerant discharged from the compressor 1, the expander 3 that recovers the expansion energy of the refrigerant, and the expander 3
- the evaporator 5 that evaporates the refrigerant is sequentially connected in series via a pipe, and the bypass circuit 7 that bypasses the expander 3 and the on-off valve 8 disposed in the bypass circuit 7 flow into the expander 3.
- coolant flow rate adjustment means which adjusts the refrigerant
- carbon dioxide is enclosed as a refrigerant.
- the compressor 1 is started by the controller 22 in step S2 with the on-off valve 8 closed in step S1.
- the room temperature is detected by the room temperature detector (ambient temperature detector) 16 installed in the vicinity of the radiator 2, and the room temperature detected by the room temperature detector 16 in step S4.
- set temperature Ta If it is determined that the detected room temperature is lower than the set temperature Ta, the process returns to step S3.On the other hand, if the detected room temperature is determined to be higher than the set temperature Ta, the process proceeds to step S5, where In order to adjust the heating capacity of the radiator 2 arranged, the compressor 1 is stopped by the controller 22. At the same time, the opening / closing valve 8 is controlled by the controller 22 at the same time.
- the refrigerant preferentially flows into the bypass circuit 7 side.
- the bypass circuit 7 side since the circuit on the expander 3 side has a larger flow path resistance than the bypass circuit 7, the refrigerant preferentially flows into the bypass circuit 7 side.
- a small amount of refrigerant flows into the expander 3 most of the refrigerant passes through the bypass circuit 7 side, so if the amount of refrigerant flowing into the expander 3 can be reduced, the heat radiation side pressure reduced by force is reduced. And the safety of the refrigeration cycle apparatus can be improved.
- FIG. 6 shows a schematic diagram of a refrigeration cycle apparatus according to Embodiment 3 of the present invention.
- symbol is attached
- the description of components common to those in Fig. 1 is omitted.
- the radiator 2 that dissipates the refrigerant discharged from the compressor, the expander 3 that recovers the expansion energy of the refrigerant, and the expander 3
- the evaporator 5 that evaporates the refrigerant is connected in series via a pipe, and a bypass circuit 10 that bypasses the expander 3 and a flow path that passes through the bypass circuit 10 and a flow path that passes through the expander 3 are connected.
- the switching three-way valve 9 is provided as a refrigerant flow rate adjusting means for adjusting the amount of refrigerant flowing into the expander 3. Further, carbon dioxide as a refrigerant is enclosed.
- step S13 If it is determined that the detected internal temperature is equal to or higher than the set temperature Tb, the process returns to step S13.On the other hand, if the detected internal temperature is determined to be lower than the set temperature Tb, the process proceeds to step S15, and the interior The compressor 1 is stopped by the controller 23 in order to adjust the cooling capacity of the evaporator 5 arranged in the above. At the same time, the controller 23 controls the three-way valve 9 to switch the three-way valve 9 so that the flow path on the bypass circuit 10 side is opened and the flow path on the expander 3 side is closed.
- the circuit on the expander 3 side is shut off and the refrigerant is controlled to pass through the bypass circuit 10 side.
- the amount of refrigerant that dissolves in the oil in the expander 3 can be greatly reduced, and the pressure on the radiator side can be reduced, making the refrigeration cycle equipment safer. Can increase the sex.
- step S16 the internal temperature detector 17 detects the internal temperature, and in step S17, the internal temperature detected by the internal temperature detector 17 is compared with the set temperature Tb. If it is determined that the detected chamber temperature is lower than the set temperature Tb, the process returns to step S16.On the other hand, if the detected chamber temperature is determined to be equal to or higher than the set temperature Tb, the process returns to step S11 and the three-way valve 9 is turned on. Control.
- the refrigeration cycle apparatus when used as a refrigerator, the refrigeration cycle apparatus is restarted even when the start / stop of the compressor 1 is repeated in order to converge the internal temperature near the set temperature. Insufficient refrigerant circulation and damage to the sliding surface of the expander 3 can be avoided.
- an evaporation temperature detector for detecting the evaporation temperature of the refrigerant in the evaporator 5 is provided to replace the internal temperature detector. Is also possible.
- Embodiment 3 the stop operation of the compressor 1 has been described as the case where the internal temperature detector detects a temperature lower than the set temperature. However, the case where the user selects the stop of the refrigeration cycle apparatus. Is the same.
- FIG. 8 shows a schematic diagram of a refrigeration cycle apparatus according to Embodiment 4 of the present invention.
- symbol is attached
- the description of components common to those in Fig. 1 is omitted.
- a compressor 1 that compresses the refrigerant, a radiator 2 that radiates the refrigerant discharged from the compressor 1, a first on-off valve 11, and an expander that recovers the expansion energy of the refrigerant 3 and an evaporator 5 for evaporating the refrigerant from the expander 3 are sequentially connected in series via a pipe, and a bypass circuit 13 for bypassing the expander 3 is provided, and a second on-off valve is provided in the bypass circuit 13
- the first on-off valve 11, the second on-off valve 12, and the bypass circuit 13 function as refrigerant flow rate adjusting means for adjusting the amount of refrigerant flowing into the expander 3.
- a compressor discharge temperature detector 14 is provided between the compressor 1 and the radiator 2 to detect the discharge temperature of the compressor 1. Carbon dioxide is enclosed as a refrigerant.
- step S21 With the first on-off valve 11 opened and the second on-off valve 12 closed in step S21, the compressor 1 is started by the controller 22 in step S22. In the next step S23, the discharge temperature of the compressor 1 is detected by the compressor discharge temperature detector 14, and in step S24, the discharge temperature detected by the compressor discharge temperature detector 14 and the set temperature Tc are compared. . If it is determined that the detected discharge temperature is lower than the set temperature Tc, the process returns to step S23.On the other hand, if the detected discharge temperature is determined to be equal to or higher than the set temperature Tc, the process proceeds to step S25, and compressor protection is performed. Therefore, the compressor 1 is stopped by the controller 24. At this time, close control of the first on-off valve 11 and open control of the second on-off valve 12 are performed almost simultaneously.
- the flow path of the refrigerant flowing into the expander 3 is blocked, and the refrigerant passes through the bypass circuit 13 and flows into the evaporator 5. Therefore, since the refrigerant flowing into the expander 3 can be shut off when the compressor 1 is stopped, the amount of refrigerant dissolved in the oil in the expander 3 can be greatly reduced as compared with the conventional example.
- step S26 the discharge temperature of the compressor 1 is detected by the compressor discharge temperature detector 14, and in step S27, the discharge temperature detected by the compressor discharge temperature detector 14 is compared with the set temperature Tc. To do. It is judged that the detected discharge temperature is higher than the set temperature Tc. If it is determined that the detected discharge temperature is lower than the set temperature Tc, the process returns to step S21 to control the first on-off valve 11 and the second on-off valve 12.
- the stop operation of the compressor 1 has been described as a case where the compressor discharge temperature detector 14 detects a set temperature or higher. However, when the user selects the stop of the refrigeration cycle apparatus. The same is true even if you enter.
- a compressor discharge temperature detector 14 is provided between the compressor 1 and the radiator 2, and based on the discharge temperature of the compressor 1 detected by the compressor discharge temperature detector 14.
- the compressor 1 and the first and second on-off valves 11 and 12 are controlled, but instead of the compressor discharge temperature detector 14, the compressor discharge pressure is connected between the compressor 1 and the radiator 2. It is also possible to provide a detector and control the compressor 1 and the first and second on-off valves 11 and 12 based on the discharge pressure of the compressor 1 detected by the compressor discharge pressure detector.
- the refrigerant flowing into the expander 3 based on the discharge temperature of the compressor 1 detected by the compressor discharge temperature detector 14 or the discharge pressure of the compressor 1 detected by the compressor discharge pressure detector.
- each of these detectors reduces the amount of refrigerant flowing into the expander 3 using a plurality of detectors connected by force if applicable to any of the second to fourth embodiments. Can be reduced.
- the refrigeration cycle apparatus can reduce the amount of refrigerant that flows into the expander and dissolves in oil when the compressor is stopped, as compared with the conventional example. Insufficient amount of cooling medium and damage to expander sliding surface can be avoided, so it can be used for a wide range of equipment such as water heaters, air conditioners, vending machines, household refrigerators, commercial refrigerators, freezers, ice makers, etc. Applicable.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Air Conditioning Control Device (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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JP2007528230A JP4912308B2 (ja) | 2005-05-06 | 2006-04-27 | 冷凍サイクル装置 |
US11/913,400 US7886550B2 (en) | 2005-05-06 | 2006-04-27 | Refrigerating machine |
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JP2005135060 | 2005-05-06 | ||
JP2005-135060 | 2005-05-06 |
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WO2006120922A1 true WO2006120922A1 (ja) | 2006-11-16 |
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PCT/JP2006/308875 WO2006120922A1 (ja) | 2005-05-06 | 2006-04-27 | 冷凍サイクル装置 |
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US (1) | US7886550B2 (ja) |
JP (1) | JP4912308B2 (ja) |
CN (1) | CN100575817C (ja) |
WO (1) | WO2006120922A1 (ja) |
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WO2009098900A1 (ja) * | 2008-02-06 | 2009-08-13 | Daikin Industries, Ltd. | 冷凍装置 |
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JP2010065855A (ja) * | 2008-09-08 | 2010-03-25 | Kobe Steel Ltd | アンモニア冷凍装置 |
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WO2011121963A1 (ja) * | 2010-03-31 | 2011-10-06 | ダイキン工業株式会社 | 冷凍装置 |
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Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5921461U (ja) * | 1982-07-30 | 1984-02-09 | 株式会社東芝 | 冷凍サイクル装置 |
JPH0646260U (ja) * | 1992-11-19 | 1994-06-24 | ホシザキ電機株式会社 | 冷却装置 |
JPH0719678A (ja) * | 1993-06-30 | 1995-01-20 | Toshiba Corp | 空気調和機の制御装置 |
JPH0741359U (ja) * | 1993-12-22 | 1995-07-21 | カルソニック株式会社 | 自動車用空気調和装置 |
JPH11132577A (ja) * | 1997-10-28 | 1999-05-21 | Toshiba Corp | 冷蔵庫の冷凍サイクル |
JP2001116371A (ja) * | 1999-10-20 | 2001-04-27 | Daikin Ind Ltd | 空気調和装置 |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2434593A (en) * | 1946-02-02 | 1948-01-13 | Carrier Corp | Refrigeration system including a load control apparatus |
US3934424A (en) * | 1973-12-07 | 1976-01-27 | Enserch Corporation | Refrigerant expander compressor |
JPS6025222B2 (ja) | 1982-07-26 | 1985-06-17 | 本田技研工業株式会社 | 繊維強化金属材料の加圧鋳造方法 |
JPH0448160A (ja) * | 1990-06-14 | 1992-02-18 | Hitachi Ltd | 冷凍サイクル装置 |
JPH05106922A (ja) * | 1991-10-18 | 1993-04-27 | Hitachi Ltd | 冷凍装置の制御方式 |
JPH0646260A (ja) | 1992-07-23 | 1994-02-18 | Fuji Xerox Co Ltd | 画像読み取り装置 |
JPH0741359A (ja) | 1993-07-30 | 1995-02-10 | Asahi Glass Co Ltd | 静電チャック用セラミックス及びその製造用組成物 |
JP4207340B2 (ja) * | 1999-03-15 | 2009-01-14 | 株式会社デンソー | 冷凍サイクル |
US6272871B1 (en) * | 2000-03-30 | 2001-08-14 | Nissan Technical Center North America | Air conditioner with energy recovery device |
US6595024B1 (en) * | 2002-06-25 | 2003-07-22 | Carrier Corporation | Expressor capacity control |
US6913076B1 (en) * | 2002-07-17 | 2005-07-05 | Energent Corporation | High temperature heat pump |
US6662576B1 (en) * | 2002-09-23 | 2003-12-16 | Vai Holdings Llc | Refrigeration system with de-superheating bypass |
JP4090317B2 (ja) * | 2002-09-25 | 2008-05-28 | 株式会社テージーケー | 電磁弁付膨張弁 |
EP1607699B1 (en) * | 2004-06-10 | 2008-05-14 | Micheletti Impianti S.R.L. | Refrigeration plant |
NL1026728C2 (nl) * | 2004-07-26 | 2006-01-31 | Antonie Bonte | Verbetering van koelsystemen. |
JP2009052752A (ja) * | 2005-12-19 | 2009-03-12 | Panasonic Corp | 冷凍サイクル装置 |
-
2006
- 2006-04-27 JP JP2007528230A patent/JP4912308B2/ja not_active Expired - Fee Related
- 2006-04-27 WO PCT/JP2006/308875 patent/WO2006120922A1/ja active Application Filing
- 2006-04-27 CN CN200680015476A patent/CN100575817C/zh not_active Expired - Fee Related
- 2006-04-27 US US11/913,400 patent/US7886550B2/en not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5921461U (ja) * | 1982-07-30 | 1984-02-09 | 株式会社東芝 | 冷凍サイクル装置 |
JPH0646260U (ja) * | 1992-11-19 | 1994-06-24 | ホシザキ電機株式会社 | 冷却装置 |
JPH0719678A (ja) * | 1993-06-30 | 1995-01-20 | Toshiba Corp | 空気調和機の制御装置 |
JPH0741359U (ja) * | 1993-12-22 | 1995-07-21 | カルソニック株式会社 | 自動車用空気調和装置 |
JPH11132577A (ja) * | 1997-10-28 | 1999-05-21 | Toshiba Corp | 冷蔵庫の冷凍サイクル |
JP2001116371A (ja) * | 1999-10-20 | 2001-04-27 | Daikin Ind Ltd | 空気調和装置 |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008261568A (ja) * | 2007-04-12 | 2008-10-30 | Daikin Ind Ltd | 膨張弁及び膨張弁を備えた動力回収装置 |
WO2009098900A1 (ja) * | 2008-02-06 | 2009-08-13 | Daikin Industries, Ltd. | 冷凍装置 |
WO2009098899A1 (ja) * | 2008-02-06 | 2009-08-13 | Daikin Industries, Ltd. | 冷凍装置 |
JP2010065855A (ja) * | 2008-09-08 | 2010-03-25 | Kobe Steel Ltd | アンモニア冷凍装置 |
JP2010249457A (ja) * | 2009-04-17 | 2010-11-04 | Fuji Electric Retail Systems Co Ltd | 冷媒回路装置 |
WO2011121963A1 (ja) * | 2010-03-31 | 2011-10-06 | ダイキン工業株式会社 | 冷凍装置 |
JP2011214779A (ja) * | 2010-03-31 | 2011-10-27 | Daikin Industries Ltd | 冷凍装置 |
US8966920B2 (en) | 2010-03-31 | 2015-03-03 | Daikin Industries, Ltd. | Refrigeration system |
WO2012042698A1 (ja) * | 2010-09-29 | 2012-04-05 | 三菱電機株式会社 | 冷凍空調装置 |
JPWO2012042698A1 (ja) * | 2010-09-29 | 2014-02-03 | 三菱電機株式会社 | 冷凍空調装置 |
Also Published As
Publication number | Publication date |
---|---|
CN100575817C (zh) | 2009-12-30 |
CN101171465A (zh) | 2008-04-30 |
JP4912308B2 (ja) | 2012-04-11 |
US20090031738A1 (en) | 2009-02-05 |
JPWO2006120922A1 (ja) | 2008-12-18 |
US7886550B2 (en) | 2011-02-15 |
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