WO2015029206A1 - 冷凍サイクル装置 - Google Patents

冷凍サイクル装置 Download PDF

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Publication number
WO2015029206A1
WO2015029206A1 PCT/JP2013/073257 JP2013073257W WO2015029206A1 WO 2015029206 A1 WO2015029206 A1 WO 2015029206A1 JP 2013073257 W JP2013073257 W JP 2013073257W WO 2015029206 A1 WO2015029206 A1 WO 2015029206A1
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Prior art keywords
pressure
compressor
pipe
refrigerant
gas cooler
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PCT/JP2013/073257
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English (en)
French (fr)
Japanese (ja)
Inventor
亮 築山
大林　誠善
仁隆 門脇
阿部　敏郎
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP13892679.5A priority Critical patent/EP3040653A4/de
Priority to PCT/JP2013/073257 priority patent/WO2015029206A1/ja
Priority to JP2015533884A priority patent/JP6080959B2/ja
Publication of WO2015029206A1 publication Critical patent/WO2015029206A1/ja

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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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • 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
    • 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
    • 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
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • 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
    • F25B2500/12—Sound
    • 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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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

Definitions

  • the present invention relates to a refrigeration cycle apparatus.
  • the high-pressure side CO 2 discharged from the compressor has a characteristic of being in a supercritical state, unlike a fluorocarbon refrigerant. That is, the CO 2 in the supercritical state does not condense when heat is given to other fluids (for example, water, air, refrigerant, etc.) by heat exchange, and remains in the supercritical state. Since CO 2 having such characteristics has little loss due to state transition, it is suitable for heat pump devices that require high temperatures. Therefore, using CO 2 as a refrigerant, to take advantage of the CO 2, the heat pump water heater has been proposed that the water was set to raise boiling to a high temperature above 90 ° C..
  • a refrigeration cycle apparatus in which the refrigerant is in a supercritical state on the high-pressure side generally includes a main circuit in which a compressor, a gas cooler, a decompression device, and an evaporator are connected via a pipe, and the compressor and the gas cooler in the main circuit. And a pressure detection circuit for detecting the refrigerant pressure (high pressure).
  • the pressure detection circuit includes a pressure detection pipe branched from the main circuit at a branch portion provided between the compressor and the gas cooler in the main circuit, and a pressure detector (pressure sensor, Pressure switch, etc.).
  • the pressure detection pipe is generally constituted by a pipe having a diameter smaller than that of the main circuit. This is because when a constant speed compressor driven by a commercial power source is used as the compressor, the pressure switch will malfunction due to a temporary increase in the high pressure in the main circuit when the refrigerant circulation rate suddenly increases during startup. This is because a capillary or the like is used for the pressure detection pipe in order to mitigate the increase in the detection pressure so as not to operate. The same can be said for the CO 2 refrigerant used in the supercritical state. Even when a compressor driven by an inverter is used, a temporary high pressure increase occurs when the frequency of the inverter power supply is greatly changed upward (high frequency side).
  • FIG. 12 is a graph showing an example of a change over time in the refrigerant pressure at each position of a general refrigeration cycle apparatus when the refrigerant is used in a supercritical state such as a CO 2 refrigerant.
  • the horizontal axis of the graph represents elapsed time (seconds) from a predetermined reference time, and the vertical axis represents pressure (MPa).
  • Line a shows the pressure change in the vicinity of the pressure sensor on the high pressure side
  • line b shows the pressure change on the upstream side of the capillary tube (pressure detection pipe) connected to the pressure switch on the high pressure side
  • line c shows the high pressure.
  • the pressure change at the service port on the side is shown, and the line d shows the pressure change at the outlet of the muffler provided on the downstream side of the compressor.
  • the drive frequency of the compressor has been reduced from 96 Hz to 86 Hz at an elapsed time of 48 seconds.
  • pressure pulsation occurs at any position of the refrigeration cycle apparatus, and the period of pulsation is about 10 ms.
  • the pulsation width at an elapsed time of 45 seconds is 1.927 MPa near the pressure sensor (line a), 0.40 MPa upstream of the capillary tube (line b), and 0.32 MPa at the service port. Yes (line c), 0.093 MPa at the muffler outlet (line d).
  • the pulsation width at an elapsed time of 57 seconds (after the compressor is decelerated) is 3.90 MPa in the vicinity of the pressure sensor (line a) and 0.44 MPa upstream of the capillary tube (line b).
  • the pressure pulsation is amplified in the pressure detection pipe, and it is difficult to accurately detect the refrigerant pressure with the pressure detector arranged at the terminal portion of the pressure detection pipe. There was a problem that there was.
  • the present invention has been made to solve the above-described problems, and an object thereof is to provide a refrigeration cycle apparatus that can detect the refrigerant pressure more accurately.
  • the refrigeration cycle apparatus includes a main circuit in which at least a compressor, a gas cooler, a decompression device, and an evaporator are connected via a pipe and circulates a refrigerant that is in a supercritical state on the high pressure side, It has a pressure detector for detecting the refrigerant pressure between the compressor and the gas cooler, and pulsation suppressing means for suppressing the pulsation of the refrigerant pressure detected by the pressure detector.
  • the refrigerant pressure can be detected more accurately.
  • FIG. 1 is a refrigerant circuit diagram illustrating an example of the configuration of the refrigeration cycle apparatus 1 according to the present embodiment.
  • a refrigeration cycle apparatus heat pump apparatus
  • a heat pump hot water supply apparatus will be described as an example of the refrigeration cycle apparatus 1.
  • the dimensional relationship and shape of each component may differ from the actual ones.
  • the refrigeration cycle apparatus 1 includes a compressor 11, a gas cooler 12, a decompressor 13, and an evaporator 14 connected via a pipe, and a refrigerant (for example, CO 2 ) that becomes a supercritical state on the high pressure side.
  • a refrigerant for example, CO 2
  • the compressor 11 is a fluid machine that sucks low-temperature and low-pressure refrigerant, compresses the drawn refrigerant to a supercritical pressure, and discharges the refrigerant as a high-temperature and high-pressure refrigerant in a supercritical state.
  • an inverter power source that can change the driving frequency of the compressor 11 within a predetermined range (for example, about 30 to 100 Hz) is used as the power source supplied to the compressor 11.
  • the gas cooler 12 is a water-side heat exchanger that cools the refrigerant discharged from the compressor 11 and heats the external fluid by heat exchange with an external fluid (in this example, circulating water for hot water supply).
  • the refrigerant cooled by the gas cooler 12 flows out of the gas cooler 12 in a supercritical state without condensing.
  • the decompression device 13 decompresses and expands the refrigerant cooled by the gas cooler 12, and flows it out as a low-temperature and low-pressure gas-liquid two-phase refrigerant.
  • an electronic expansion valve is used as the decompression device 13.
  • the evaporator 14 is an air-side heat exchanger that evaporates the gas-liquid two-phase refrigerant flowing out from the decompression device 13 by heat exchange with an external fluid (air in this example).
  • the main circuit 10 is provided with a high / low pressure heat exchanger 17 for exchanging heat between the high temperature / high pressure refrigerant flowing out from the gas cooler 12 and the low temperature / low pressure refrigerant flowing out from the evaporator 14.
  • the high-low pressure heat exchanger 17 is provided with a high-pressure refrigerant channel through which high-temperature and high-pressure refrigerant flowing out from the gas cooler 12 flows, and a low-pressure refrigerant channel through which low-temperature and low-pressure refrigerant flowing out from the evaporator 14 flows. Yes.
  • a strainer 16 is provided downstream of the high-pressure refrigerant flow path of the high-low pressure heat exchanger 17 and upstream of the decompression device 13.
  • a strainer 15 is provided downstream of the low-pressure refrigerant flow path of the high-low pressure heat exchanger 17 and upstream of the compressor 11.
  • a muffler 20 is provided in the main circuit 10 downstream of the compressor 11 and upstream of the gas cooler 12.
  • An oil recovery circuit 21 that recovers refrigeration oil and returns it to the suction side of the compressor 11 is connected to the muffler 20.
  • the oil recovery circuit 21 includes a muffler 20, a merging portion 28 provided on the downstream side of the low-pressure refrigerant flow path of the high-low pressure heat exchanger 17 and upstream of the compressor 11 (upstream side of the strainer 15), Are connected.
  • a heat exchanger 22 that heats hot water (circulated water) by heat exchange with high-temperature refrigeration oil and a bypass circuit 23 that bypasses the heat exchanger 22 are provided in parallel. Yes.
  • the bypass circuit 23 is provided with an electromagnetic valve 24 that opens and closes the bypass circuit 23.
  • a strainer 25 is provided on the upstream side of the branching portion that branches into the heat exchanger 22 and the bypass circuit 23.
  • a branch pipe 26 branches from the oil recovery circuit 21.
  • the branch pipe 26 is provided with a service valve 27a and a service port 27b. Further, a pressure sensor 29 that further branches from the branch pipe 26 and detects the refrigerant pressure on the low pressure side is provided via the capillary 30.
  • a branch portion 31 provided downstream of the muffler 20 of the main circuit 10 and upstream of the gas cooler 12, and provided downstream of the gas cooler 12 and upstream of the high-pressure refrigerant flow path of the high-low pressure heat exchanger 17.
  • the joining portion 32 is connected by a bypass circuit 33 that bypasses the gas cooler 12.
  • the bypass circuit 33 is provided with an electromagnetic valve 34 for opening and closing the bypass circuit 33, and a strainer 35 is provided on the upstream side of the electromagnetic valve 34.
  • the bypass circuit 38 is provided with an electromagnetic valve 39 that opens and closes the bypass circuit 38, and a strainer 40 is provided upstream of the electromagnetic valve 39.
  • a bypass circuit 43 that bypasses the decompression device 13 is connected to the junction 42 provided on the upstream side of the evaporator 14 (upstream of the junction 37).
  • the bypass circuit 43 includes an internal heat exchanger 45 that exchanges heat with a refrigerant that flows downstream of the compressor 11 of the main circuit 10 and upstream of the gas cooler 12, and an electromagnetic valve 44 that opens and closes the bypass circuit 43. , Is provided.
  • a pressure detection circuit 110 is provided in a branch portion 111 provided downstream of the compressor 11 of the main circuit 10 (downstream of the branch portion 31) and upstream of the gas cooler 12 (upstream of the branch portion 36). Is connected.
  • the pressure detection circuit 110 includes a pressure switch 112 and a pressure detection pipe 114 that connects the branch portion 111 and the pressure switch 112.
  • the pressure detection circuit 110 includes a pressure sensor 113 and a pressure detection pipe that branches from the pressure detection pipe 114 at a branch part 116 provided in the pressure detection pipe 114 and connects between the branch part 116 and the pressure sensor 113.
  • the pressure switch 112 is provided at the terminal of the pressure detection pipe 114, and the pressure sensor 113 is provided at the terminal of the pressure detection pipe 115.
  • Both the pressure switch 112 and the pressure sensor 113 have a function as a pressure detector that detects the refrigerant pressure (discharge pressure) between the compressor 11 and the gas cooler 12 of the main circuit 10.
  • the pressure switch 112 cuts off the power supply to the compressor 11 when the refrigerant pressure between the compressor 11 and the gas cooler 12 becomes abnormally high.
  • the pressure sensor 113 detects the refrigerant pressure between the compressor 11 and the gas cooler 12 and outputs a detection signal to the control unit 100 described later.
  • the pressure detection pipe 114 between the branch part 111 of the main circuit 10 and the pressure switch 112 has the same inner diameter (for example, ⁇ 6.35) and is not contracted. Further, the pressure detection pipes 114 and 115 between the branch part 111 of the main circuit 10 and the pressure sensor 113 have the same inner diameter (for example, ⁇ 6.35) and are not contracted. That is, the pressure detection pipes 114 and 115 do not have a contraction pipe part from the branch part 111 to the pressure switch 112 or the pressure sensor 113.
  • the pipe cross-sectional area of the pipe is defined. Is the part that decreases on the way.
  • the flow path cross-sectional areas of the pressure detection pipes 114 and 115 are increased. There is no decreasing part.
  • a branch pipe 118 is branched from a branch portion 117 provided in the pressure detection pipe 114.
  • the branch pipe 118 is provided with a service valve 121a and a service port 121b.
  • the refrigeration cycle apparatus 1 has various temperature sensors.
  • a temperature sensor 71 for detecting the discharge temperature of the compressor 11 is provided on the downstream side of the compressor 11 of the main circuit 10 and on the upstream side of the muffler 20.
  • a temperature sensor 72 that detects the outlet temperature of the gas cooler 12 is provided upstream of the high-pressure refrigerant flow path of the heat exchanger 17 (upstream of the merging section 32), and downstream of the decompression device 13 (from the merging section 42).
  • a temperature sensor 74 that is provided upstream of the low-pressure refrigerant flow path of the evaporator 17 and detects the outlet temperature of the evaporator 14, and is downstream of the low-pressure refrigerant flow path of the high-low pressure heat exchanger 17 and upstream of the compressor 11.
  • the temperature sensor 75 for detecting an intake temperature of the compressor 11, provided in the vicinity of the evaporator 14, includes such a temperature sensor 76 for detecting the outside air temperature. These temperature sensors output a temperature detection signal to the control unit 100 described later.
  • the refrigeration cycle apparatus 1 has a control unit 100.
  • the control unit 100 in this example is a microcomputer including a CPU, a ROM, a RAM, an I / O port, and the like.
  • the control unit 100 controls the compressor 11 and the decompression device 13 and the like based on detection signals input from the temperature sensors 71, 72, 73, 74, 75, and 76, the pressure sensors 29 and 113, and the like. ing.
  • the heat pump type hot water supply apparatus has a boiling circuit 50 that uses the refrigeration cycle apparatus 1 to boil water in a hot water storage tank (not shown).
  • the boiling circuit 50 connects between the lower part and the upper part of the hot water storage tank.
  • the boiling circuit 50 takes out low-temperature water from the lower part of the hot water storage tank, and heats it up by heat exchange with the refrigerating machine oil in the heat exchanger 22 and heat exchange with the refrigerant in the gas cooler 12, and as the hot water, the upper part of the hot water storage tank. It comes to return to.
  • a circulation pump 51 is provided on the upstream side of the heat exchanger 22 and the gas cooler 12, and sends the water in the lower part of the hot water tank to the upper part of the hot water tank as circulating water.
  • an electric valve 52 that adjusts the flow rate of the circulating water
  • a check valve 53 disposed on the downstream side of the electric valve 52
  • a pressure reducing valve 54 disposed on the side.
  • a strainer 55 is provided downstream of the electric valve 52 and upstream of the check valve 53.
  • a water supply circuit 57 for supplying tap water to the boiling circuit 50 is connected to a junction 56 provided downstream of the pressure reducing valve 54 and upstream of the circulation pump 51 in the boiling circuit 50. Yes.
  • the water supply circuit 57 includes an electric valve 58 for adjusting the flow rate of tap water, a check valve 59 disposed on the downstream side of the electric valve 58, a pressure reducing valve 60 disposed on the downstream side of the check valve 59, Is provided.
  • a strainer 61 is provided downstream of the electric valve 58 and upstream of the check valve 59.
  • An electric valve 62 for adjusting the flow rate of the circulating water is provided in the boiling circuit 50 downstream of the circulation pump 51 and upstream of the heat exchanger 22.
  • a branch pipe provided with a relief valve 63 is connected downstream of the circulation pump 51 and upstream of the electric valve 62.
  • a flow rate sensor 64 that detects the flow rate of the circulating water is provided downstream of the motor-operated valve 62 and upstream of the heat exchanger 22.
  • a temperature sensor 77 for detecting the temperature of the circulating water before boiling is provided in the boiling circuit 50 downstream of the circulation pump 51 and upstream of the heat exchanger 22 (upstream of the electric valve 62). It has been. Further, a temperature sensor 78 for detecting the temperature of the circulating water after boiling is provided in the boiling circuit 50 on the downstream side of the gas cooler 12.
  • the above-described temperature sensors 77 and 78, the flow rate sensor 64, and the like output detection signals to the control unit (not shown) of the heat pump type hot water supply apparatus or the control unit 100 of the refrigeration cycle apparatus 1.
  • FIG. 2 shows the configuration of the pressure detection circuit 110 of the present embodiment.
  • FIG. 2 shows a pressure detection circuit 110 in which the configuration is simplified compared to the pressure detection circuit 110 shown in FIG. 1 and only the pressure sensor 113 is provided as a pressure detector.
  • a pressure detection circuit 110 shown in FIG. 2 includes a pressure sensor 113 that detects a refrigerant pressure on the high-pressure side, and a branch portion 111 that is provided downstream of the compressor 11 and upstream of the gas cooler 12 in the main circuit 10. And a pressure detection pipe 115 connecting between the pressure sensor 113 and the pressure sensor 113.
  • the pressure detection pipe 115 branches at a branching portion 111 in a direction perpendicular to the main circuit 10. Further, the pressure detection pipe 115 has a straight tubular structure without branching.
  • the pressure sensor 113 is provided at the terminal of the pressure detection pipe 115.
  • the pressure detection pipe 115 from the branch part 111 to the pressure sensor 113 has the same inner diameter and is not contracted.
  • FIG. 3 shows a configuration of a pressure detection circuit 210 having a contraction section 119 in the pressure detection pipe 115.
  • the pressure detection circuit 210 shown in FIG. 3 is a pressure sensor 113 that detects the refrigerant pressure on the high pressure side, and a pressure that connects between the branch portion 111 and the pressure sensor 113. And a detection pipe 115.
  • the pressure detection pipe 115 of the pressure detection circuit 210 is different from the pressure detection pipe 115 shown in FIG. 2 in that the contraction pipe part 119 is provided in a part of the pipe line from the branch part 111 to the pressure sensor 113. Have.
  • the pipe diameter (channel cross-sectional area) of the pressure detection pipe 115 at the terminal portion where the pressure sensor 113 is provided is larger than the pipe diameter (channel cross-sectional area) of the pressure detection pipe 115 in the vicinity of the branch portion 111. It is getting smaller.
  • the refrigerant used in the refrigeration cycle apparatus 1 of the present embodiment is in a supercritical state on the high pressure side.
  • Supercritical refrigerants have very low compressibility.
  • the change rate ⁇ (0 ⁇ ) of the cross-sectional area of the pipe (flow path) before and after the contraction pipe part 119 is closer to the terminal side than the contraction pipe part 119.
  • Pressure pulsation is amplified in inverse proportion to ⁇ ⁇ 1). Therefore, in the pressure detection circuit 210 shown in FIG. 3, it may be difficult to accurately detect the refrigerant pressure with the pressure sensor 113 provided at the terminal of the pressure detection pipe 115.
  • the pressure detection pipe 115 is not provided with a contraction section. For this reason, in the pressure detection pipe 115 of the pressure detection circuit 110, the cross-sectional area of the flow path through which the refrigerant flows does not change from the branch portion 111 to the pressure sensor 113 and is constant. Thereby, the pressure pulsation in the terminal part of the pressure detection piping 115 can be suppressed. Therefore, according to the present embodiment, the pressure sensor 113 can more accurately detect the refrigerant pressure (discharge pressure).
  • At least the compressor 11, the gas cooler 12, the decompression device 13, and the evaporator 14 are connected via a pipe, and are in a supercritical state on the high pressure side.
  • a main circuit 10 for circulating the gas a pressure detector (for example, a pressure sensor 113, a pressure switch 112) for detecting a refrigerant pressure between the compressor 11 and the gas cooler 12 in the main circuit 10, and a pressure detector.
  • pulsation suppression means for suppressing pulsation of the refrigerant pressure (for example, pressure detection pipe 115 not provided with a contraction pipe portion).
  • the refrigerant pressure between the compressor 11 and the gas cooler 12 in the main circuit 10 can be detected more accurately.
  • the pulsation suppressing means includes a branch portion 111 provided between the compressor 11 and the gas cooler 12 in the main circuit 10 and a pressure detector (for example, a pressure sensor). 113, pressure switch 112), and a pressure detection pipe 115 that does not have a contraction pipe part in which the cross-sectional area of the flow path decreases midway between the branch part 111 and the pressure detector. It is characterized by.
  • FIG. 4 is a diagram showing a configuration of the pressure detection circuit 110 of the refrigeration cycle apparatus according to the present embodiment.
  • symbol is attached
  • the pressure detection pipe 115 of the pressure detection circuit 110 in the present embodiment has a contraction pipe part 119 in a part of the pipe line from the branch part 111 to the pressure sensor 113. Yes.
  • the path length A of the pressure detection pipe 115 between the branch part 111 and the contracted pipe part 119 is 100 mm or less. The reason why the path length A is set to 100 mm or less will be described below.
  • FIG. 5 is a graph showing the correlation between the temperature and density of the CO 2 refrigerant in a high pressure state (12 MPa and 13 MPa).
  • the horizontal axis of the graph represents the CO 2 refrigerant temperature (° C.)
  • the vertical axis represents the density of the CO 2 refrigerant (kg / m 3).
  • the CO 2 refrigerant in a high pressure state has a property that the density increases as the temperature decreases.
  • the temperature range of the CO 2 refrigerant in the pipe (main pipe) of the main circuit 10 is about 30 to 100 ° C.
  • the pressure detection pipe 115 is smaller in diameter than the pipe of the main circuit 10 and has a large heat loss per unit flow path length.
  • the temperature of the refrigerant in the pressure detection pipe 115 decreases as the distance from the branch portion 111 increases. For example, if the refrigerant temperature in the main pipe is 100 ° C., the refrigerant temperature in the pressure detection pipe 115 becomes lower than 100 ° C., and decreases monotonically as the distance from the main pipe (distance from the branch portion 111) increases. (See FIG. 5). Therefore, when the path length A between the branch portion 111 and the contracted tube portion 119 exceeds a predetermined value (for example, 100 mm), the temperature of the refrigerant between the branch portion 111 and the contracted tube portion 119 becomes lower and the density is increased. Therefore, a pressure pulsation occurs between the branch part 111 and the contracted tube part 119, and the pressure pulsation on the terminal side from the contracted tube part 119 is amplified.
  • a predetermined value for example, 100 mm
  • the path length A of the pressure detection pipe 115 between the branch part 111 and the contraction pipe part 119 is reduced. It can be kept below the value at which pressure pulsation occurs. Therefore, amplification of pressure pulsation on the terminal side from the contracted tube portion 119 can be suppressed, and pulsation of refrigerant pressure detected by the pressure sensor 113 can be suppressed.
  • the pulsation suppressing means includes the branch portion 111 provided between the compressor 11 and the gas cooler 12 in the main circuit 10 and a pressure detector (for example, , Pressure sensor 113, pressure switch 112), and pressure detection pipe 115 having a contracted tube portion 119 in which the cross-sectional area of the flow path decreases from the branch portion 111 to the pressure detector.
  • the path length A of the pressure detection pipe 115 between the branch part 111 and the contraction pipe part 119 is 100 mm or less.
  • the refrigerant pressure detected by the pressure detector can be suppressed, the refrigerant pressure can be detected more accurately.
  • FIG. 6 is a diagram showing a configuration of the pressure detection circuit 110 of the refrigeration cycle apparatus according to the present embodiment.
  • symbol is attached
  • the pressure detection pipe 115 of the pressure detection circuit 110 in the present embodiment has a contraction pipe part 119 in a part of the pipe line from the branch part 111 to the pressure sensor 113. Yes.
  • the path length A of the pressure detection pipe 115 between the branch part 111 and the contraction pipe part 119 is longer than 100 mm, for example.
  • the pressure detection circuit 110 is provided with a heater 120 that heats the pressure detection pipe 115 between the branch part 111 and the contraction pipe part 119.
  • the heater 120 heats the pressure detection pipe 115 between the branch part 111 and the contraction pipe part 119 to a temperature equal to or higher than that of the main circuit 10 in the vicinity of the branch part 111.
  • the temperature of the refrigerant between the branching portion 111 and the contracted tube portion 119 is lowered and the density is increased. Then, a pressure pulsation occurs between the branching part 111 and the contracted tube part 119, and the pressure pulsation on the terminal side from the contracted tube part 119 is amplified.
  • the pressure detection pipe 115 between the branch part 111 and the contraction pipe part 119 is heated by the heater 120.
  • coolant temperature between the branch part 111 and the contraction pipe part 119 can be prevented, and the density of the refrigerant
  • the pressure detection pipe 115 having a path length A longer than 100 mm is taken as an example, but the heater 120 may be provided in the pressure detection pipe 115 having a path length A of 100 mm or less.
  • the pulsation suppressing means includes the branch portion 111 provided between the compressor 11 and the gas cooler 12 in the main circuit 10 and a pressure detector (for example, , Pressure sensor 113, pressure switch 112), and pressure detection pipe 115 having a contracted tube portion 119 in which the cross-sectional area of the flow path decreases from the branch portion 111 to the pressure detector. And a heater 120 that heats the pressure detection pipe 115 between the branch part 111 and the contraction pipe part 119.
  • a pressure detector for example, Pressure sensor 113, pressure switch 112
  • pressure detection pipe 115 having a contracted tube portion 119 in which the cross-sectional area of the flow path decreases from the branch portion 111 to the pressure detector.
  • a heater 120 that heats the pressure detection pipe 115 between the branch part 111 and the contraction pipe part 119.
  • the refrigerant pressure detected by the pressure detector can be suppressed, the refrigerant pressure can be detected more accurately.
  • FIG. 7 is a diagram showing a configuration of the pressure detection circuit 110 of the refrigeration cycle apparatus according to the present embodiment.
  • symbol is attached
  • the pressure detection pipe 115 of the pressure detection circuit 110 in the present embodiment does not have a contraction pipe part from the branch part 111 to the pressure sensor 113.
  • the path length B of the pressure detection pipe 115 between the branch part 111 and the pressure sensor 113 (the total length of the pressure detection pipe 115) is 1000 mm or less. The reason why the path length B is set to 1000 mm or less will be described below.
  • the pressure wavelength ⁇ is obtained from the drive frequency of the compressor 11 and the speed of sound in the refrigerant.
  • FIG. 8 is a graph showing the relationship between the drive frequency of the compressor 11 and the pressure wavelength.
  • the horizontal axis of the graph represents the frequency (Hz) of the compressor 11, and the vertical axis represents the length (mm) of the pressure wavelength.
  • ((2n-1) / 4) ⁇ in FIG. 8, only 1 / 4 ⁇ and 3 / 4 ⁇ are included).
  • the path length B is longer than about 1000 mm, it always matches ((2n ⁇ 1) / 4) ⁇ at at least a part of the operating range of the compressor 11.
  • the path length B is 1000 mm or less, the frequency in the operating range of the compressor 11 does not coincide with ((2n ⁇ 1) / 4) ⁇ . Therefore, by setting the path length B to 1000 mm or less, it is possible to prevent the pressure pulsation from being maximized in the vicinity of the pressure sensor 113, so that the pulsation of the refrigerant pressure detected by the pressure sensor 113 can be suppressed. it can.
  • the pressure detection pipe 115 having no contraction pipe portion is taken as an example, but the present embodiment can also be applied to the pressure detection pipe 115 having a contraction pipe section.
  • the pulsation suppressing means includes the branch portion 111 provided between the compressor 11 and the gas cooler 12 in the main circuit 10 and a pressure detector (for example, , Pressure sensor 113 and pressure switch 112), and the path length B of the pressure detection pipe 115 between the branch portion 111 and the pressure detector is 1000 mm or less. It is what.
  • the refrigerant pressure detected by the pressure detector can be suppressed, the refrigerant pressure can be detected more accurately.
  • Embodiment 5 A refrigeration cycle apparatus according to Embodiment 5 of the present invention will be described.
  • the pulsation cycle of the refrigerant pressure in the refrigeration cycle apparatus is about 10 ms.
  • a pressure pulsation (for example, a peak pressure value) cannot be detected in a sampling period of 20 ms generally used in a conventional pressure detection algorithm, and the control of the compressor 11 is performed based on an accurate refrigerant pressure.
  • the pressure pulsation waveform is assumed to be a sine wave, and the pressure detection algorithm in the control unit 100 is defined as follows so that the refrigerant pressure can be detected more accurately.
  • FIG. 9 is a diagram for explaining a pressure detection algorithm of the refrigeration cycle apparatus according to the present embodiment.
  • the horizontal axis in FIG. 9 represents the elapsed time (ms) from power-on.
  • the sampling period for obtaining the detected value of the refrigerant pressure detected by the pressure sensor 113 is 1 ⁇ 2 of one period of the compressor 11 frequency (minimum driving frequency).
  • the sampling period is 16.7 ms or less, which is 1/2 or less of one period (33.3 ms) of the lowest driving frequency (30 Hz). Is set.
  • the sampling period is 5 ms. That is, the detected value Hpt of the refrigerant pressure is acquired at a cycle of 5 ms.
  • the average value Hpa and one piece are obtained every predetermined period (in this example, 100 ms which is 20 times the sampling period) which is N times the sampling period (where N is an integer of 2 or more).
  • the average value Hpa is an average value of N (20 in this example) detection values Hpt acquired during the predetermined period.
  • the half amplitude value Hpb is an average of absolute values of deviations from the average value Hpa in the N detection values Hpt.
  • the half amplitude value Hpb is (
  • the effective amplitude value Hpc is an average (moving) of M piece amplitude values Hpb calculated every predetermined period (in this example, the predetermined period of the past 5 times) in the past M times (where M is an integer of 2 or more). Average).
  • the amplitude peak value Hpd is ⁇ 2 times the effective amplitude value Hpc.
  • the peak pressure value Hpmpeek is the sum of the amplitude peak value Hpd and the average value Hpa.
  • the peak pressure value Hmppeak may be the sum of the amplitude peak value Hpd and the average (moving average) of the M average values Hpa calculated for the past M predetermined periods.
  • the effective amplitude value Hpc is determined to be one to four single amplitudes.
  • the average value of the values Hpb is used. That is, the effective amplitude value Hpc, the amplitude peak value Hpd, and the peak pressure value Hpmpeek are all calculated every predetermined period (100 ms) after the power is turned on.
  • the control unit 100 controls the increase / decrease of the driving frequency of the compressor 11 and the stop of the compressor 11 when an abnormal pressure is detected based on the peak pressure value Hmppeak calculated every predetermined period.
  • the pressure detection algorithm as described above can be applied to the configurations of the refrigeration cycle apparatuses according to Embodiments 1 to 4, and can also be applied to the configuration of a conventional refrigeration cycle apparatus.
  • At least the compressor 11, the gas cooler 12, the decompression device 13, and the evaporator 14 are connected via a pipe, and a refrigerant that becomes a supercritical state on the high-pressure side is used.
  • the control unit 100 sets the sampling period for obtaining the detected value Hpt of the refrigerant pressure detected by the pressure sensor 113 to 1 ⁇ 2 or less of one period of the lowest frequency of the compressor 11, and N times the sampling period ( However, the average value Hpa of the N detection values Hpt and the average of the absolute values of the deviations from the average value Hpa of the N detection values Hpt every predetermined period of time (N is an integer of 2 or more)
  • N is an integer of 2 or more
  • a certain amplitude value Hpb is calculated, and ⁇ of the moving average (amplitude effective value Hpc) of M pieces of amplitude values Hpb calculated every predetermined period of the past M times (where M is an integer of 2 or more).
  • a peak pressure value Hmppeak that is the sum of an amplitude peak value Hpd that is twice and an average value Hpa is calculated for each predetermined period, and the compressor 11 is controlled based on the peak pressure value Hmppeak. It is.
  • the refrigerant pressure can be detected more accurately, and the compressor 11 can be controlled based on the more accurate refrigerant pressure.
  • FIG. 10 is a graph showing an example of a pressure value (peak pressure value Hpmpeek) calculated in the present embodiment.
  • ⁇ indicates the pressure value before taking in
  • ⁇ indicates the average value Hpa
  • ⁇ indicates the peak pressure value Hppeak.
  • FIG. 11 is a graph showing an example of a conventional detected pressure value. In the graph, “ ⁇ ” indicates a pressure value before taking in, and “ ⁇ ” indicates a conventional detected pressure value.
  • the pressure pulsation waveform was a sine wave, the pulsation frequency was 96 Hz, the pulsation amplitude was 2 MPa, and the rate of increase in average pressure was 0.05 MPa / s.
  • the pressure pulsation cannot be detected with the conventional detected pressure value.
  • the peak pressure value Hmppeak calculated by the present embodiment is substantially equal to the value of the high pressure side peak of the pressure pulsation. Therefore, according to the present embodiment, it is possible to detect a high pressure side peak of pressure pulsation.
  • the present invention is not limited to the above embodiment, and various modifications can be made.
  • the pressure detection pipe having the same inner diameter (the same flow path cross-sectional area) from the branch part 111 to the pressure switch 112 or the pressure sensor 113 is used as the pressure detection pipe having no contraction pipe part.
  • the pipes 114 and 115 are given as examples, the present invention is not limited to this.
  • the pressure detection pipes 114 and 115 may be expanded between the branch portion 111 and the pressure switch 112 or the pressure sensor 113.
  • the pressure detection pipes 114 and 115 have a channel cross-sectional area in the middle of a range in which the channel cross-sectional area immediately before the pressure switch 112 or the pressure sensor 113 does not become smaller than the channel cross-sectional area immediately after the branch portion 111. You may have the expanding part which increases.
  • the pressure detection pipes 114 and 115 may have a pipe expansion part and a contraction pipe part within a range in which the flow path cross-sectional area immediately before the pressure switch 112 or the pressure sensor 113 does not become smaller than the flow path cross-sectional area immediately after the branch part 111. You may have.
  • Refrigeration cycle apparatus 10 Main circuit, 11 Compressor, 12 Gas cooler, 13 Depressurizer, 14 Evaporator, 15, 16, 25, 35, 40, 55, 61 Strainer, 17 High / low pressure heat exchanger, 20 Muffler, 21 Oil recovery circuit, 22 heat exchanger, 23, 33, 38 bypass circuit, 24, 34, 39, 44 solenoid valve, 26 branch piping, 27a, 121a service valve, 27b, 121b service port, 29 pressure sensor, 30 capillary, 31, 36, 41 Branch, 32, 37, 42, 56 Merge, 45 Internal heat exchanger, 50 Boiling circuit, 51 Circulation pump, 52, 58, 62 Motorized valve, 53, 59 Check valve, 54, 60 pressure reducing valve, 63 relief valve, 64 flow rate sensor, 71, 72, 73, 74, 75, 76, 77, 7 Temperature sensor, 100 control unit, 110, 210 pressure detecting circuit, 111,116,117 bifurcation 112 pressure switch, 113 a pressure sensor, 114 and 115 pressure

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  • Engineering & Computer Science (AREA)
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PCT/JP2013/073257 2013-08-30 2013-08-30 冷凍サイクル装置 WO2015029206A1 (ja)

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PCT/JP2013/073257 WO2015029206A1 (ja) 2013-08-30 2013-08-30 冷凍サイクル装置
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JPS57175970U (de) * 1981-04-30 1982-11-06
JPS58149585U (ja) * 1982-03-31 1983-10-07 三菱電機株式会社 冷凍装置
JPS60116177U (ja) * 1984-01-17 1985-08-06 三菱電機株式会社 冷凍装置等の補器
JPH03247962A (ja) * 1990-02-23 1991-11-06 Mitsubishi Electric Corp 冷凍サイクル制御方式
JP2001116372A (ja) * 1999-10-20 2001-04-27 Zexel Valeo Climate Control Corp 冷凍サイクル制御装置
JP2009229012A (ja) * 2008-03-24 2009-10-08 Daikin Ind Ltd 冷凍装置
JP2010107162A (ja) 2008-10-31 2010-05-13 Daikin Ind Ltd ヒートポンプ式給湯装置

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JPS587318Y2 (ja) * 1978-08-18 1983-02-08 三洋電機株式会社 圧力検知装置
JPS6355065U (de) * 1986-09-26 1988-04-13
JPH05180545A (ja) * 1991-12-28 1993-07-23 Mitsubishi Heavy Ind Ltd 圧力機器の取付構造
JPH09329517A (ja) * 1996-06-10 1997-12-22 Fuji Koki:Kk 圧力検出装置
JP2003222396A (ja) * 2002-01-30 2003-08-08 Daikin Ind Ltd ヒートポンプ式給湯機
JP2008045778A (ja) * 2006-08-11 2008-02-28 Daikin Ind Ltd 空気調和装置
JP2011149614A (ja) * 2010-01-21 2011-08-04 Sanyo Electric Co Ltd 冷却装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS477153Y1 (de) * 1969-12-11 1972-03-15
JPS57175970U (de) * 1981-04-30 1982-11-06
JPS58149585U (ja) * 1982-03-31 1983-10-07 三菱電機株式会社 冷凍装置
JPS60116177U (ja) * 1984-01-17 1985-08-06 三菱電機株式会社 冷凍装置等の補器
JPH03247962A (ja) * 1990-02-23 1991-11-06 Mitsubishi Electric Corp 冷凍サイクル制御方式
JP2001116372A (ja) * 1999-10-20 2001-04-27 Zexel Valeo Climate Control Corp 冷凍サイクル制御装置
JP2009229012A (ja) * 2008-03-24 2009-10-08 Daikin Ind Ltd 冷凍装置
JP2010107162A (ja) 2008-10-31 2010-05-13 Daikin Ind Ltd ヒートポンプ式給湯装置

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